Electric motor with brake, brake and process

Abstract

Electric motor (50) comprising a housing, a stator (16), a rotor (1) and a brake (550), wherein the housing comprises a flange shield (64), a stator housing (52) and a bearing shield (42), wherein the rotor (1) comprises a rotor assembly (72) and a shaft (66) which has sections of different diameters separated by shaft diameter steps, wherein the brake (550) comprises an armature disk (149), a magnet body (154) with coil (155) and a lining carrier (168) which is non-rotatably connected to the shaft (66) by means of a driver (70), wherein a brake pad (169) arranged in a pad area is arranged in a pad area and an approximately tubular brake housing part (166) surrounds the pad area in a housing-forming manner, wherein the brake pad (169) is arranged on the pad carrier (168), wherein an inner ring of a floating bearing (44) is fixed on the shaft side in an axial direction by a further shaft diameter step and the driver (70), wherein a lifting lever (53) is supported with its bearing point on the magnet body (154), the lifting lever (53) is connected to the armature disk (149) via a lifting pin screw (56) and the armature disk (149) can be pressed against the magnet body (154) by means of a hand lever (51) which protrudes radially from the electric motor (50) to the shaft (66) and is rigidly connected to the lifting lever (53), wherein a fan wheel (36) is non-rotatably connected to the shaft (36) and wherein the brake (550) and the fan wheel (36) are surrounded by a fan cover (35) forming a housing, wherein the tubular brake housing part (166) is elastically deformed at a first axial end region and is elastically deformed at a second axial end region and is clamped on the magnet body (154), wherein the air lever (53) supports its contact point on the side of the magnet body (154) facing away from the brake shield (702).

Description

[0001] The invention relates to an electric motor with a brake, a brake for an electric motor and a method for manufacturing a brake for an electric motor.

[0002] An electric motor with a brake is known from DE 198 38 171 A1. In this electric motor brake, the armature plate in the guide device is essentially rotationally fixed but axially displaceable in the direction of the shaft. The guide device fulfills a variety of functions and has a relatively complex shape with claws, openings for screws, and shoulders. Likewise, a bearing shield with a shape complementary to that of the guide ring is required.

[0003] From DE 10 2004 033 745 A1, an electric motor is known as the closest state of the art.

[0004] A series of electric motors is known from DE 10 2004 063 920 A1.

[0005] A fan wheel is known from DE 10 2004 049 125 A1.

[0006] From DE 19 14 469 C2, an adjusting device for the air clearance of a spring-actuated and electromagnetically air-ventilated single-disc brake for motors is known.

[0007] An electromagnetically actuated brake is known from DE 196 22 983 C1.

[0008] An electromagnetic brake is known from DE 89 13 767 U1.

[0009] An electromagnetic brake is known from DE 41 26 672 A1.

[0010] An electro-magnetic brake is known from DE 66 07 900 U.

[0011] A brake motor is known from DE 86 22 735 U1.

[0012] From DE 202 18 026 U1 a device for manually releasing a spring-applied brake on an electric brake motor is known.

[0013] An electric motor with a brake is known from DE 198 38 171 A1.

[0014] A series of electric motors with speed feedback is known from DE 199 24 735 A1.

[0015] The invention is therefore based on the objective of further developing an electric motor and a brake for an electric motor, so that the electric motor or the brake can be manufactured more cost-effectively and easily.

[0016] According to the invention, the problem is solved in the electric motor, the brake, or the method according to the features specified in claim 1, 3 or 12.

[0017] Key features of the invention in the electric motor are that the electric motor comprises a housing, a stator, a rotor, and a brake, wherein the housing comprises a flange shield, a stator housing, and a bearing shield, wherein the rotor comprises a rotor assembly and a shaft which has sections of different diameters separated by shaft diameter steps, wherein the brake comprises an armature disk, a magnet body with a coil, and a lining carrier non-rotatably connected to the shaft by means of a driver, wherein a brake lining is arranged in a lining area, and an approximately tubular brake housing part surrounds the lining area in a housing-forming manner, wherein the brake lining is arranged on the lining carrier, and wherein an inner ring of a floating bearing is fixed axially on the shaft side by a further shaft diameter step and the driver.wherein a lifting lever is supported at its contact point on the magnet body, the lifting lever is connected to the armature disk via a lifting pin screw, and the armature disk can be pressed against the magnet body by means of a hand lever which projects radially from the electric motor to the shaft and is rigidly connected to the lifting lever, wherein a fan wheel is non-rotatably connected to the shaft, and wherein the brake and the fan wheel are enclosed by a fan cover forming a housing.

[0018] The advantage here is that the brake can be mounted independently of the electric motor, making the electric motor and brake easier and cheaper to manufacture.

[0019] In a preferred embodiment, the flange plate is designed as a gearbox flange plate, and an oil inlet opening can be closed by a plug screw. The advantage here is that the flanged gearbox does not require an oil inlet opening, and therefore many different gearboxes can be flanged to the electric motor.

[0020] Key features of the invention for the brake are that the electromagnetically actuated brake for an electric motor comprises a brake pad arranged in a lining area and a magnetic body, wherein a tubular brake housing part is made of an elastic material such that it can be slipped over the magnetic body and the tubular brake housing part surrounds the lining area, forming a housing. An advantage of this is that the brake is easy to install and the lining area is sealed to the outside, so that brake wear debris remains within the lining area.

[0021] In an advantageous design, the elastic material conducts heat less effectively than a metal or stainless steel. The advantage here is that the brake housing component conducts heat from the magnet body to the electric motor less effectively than metal or stainless steel, thus acting as a thermal barrier.

[0022] In a further advantageous embodiment, the elastic material is an elastic rubber or silicone. The advantage here is that the brake is inexpensive and easy to manufacture. The housing component thus acts as a vibration damper and sound insulator against airborne and structure-borne noise. Silicone is also heat-resistant up to approximately 300°C.

[0023] In a further advantageous embodiment, the brake comprises a brake pad carrier, which is non-rotatably connected to a shaft of the electric motor and contains the brake pad, an axially movable and essentially non-rotatable armature disk, and a magnetic body comprising a coil. An advantage of this design is that only a small amount of mass is attached to the rotating rotor, thus enabling high motor dynamics.

[0024] In a further advantageous embodiment, the lining carrier and the armature disk, which is attracted by the magnet body against a braking force applied by helical compression springs when the coil is energized, are arranged in the lining area between the magnet body and the brake shield. When the coil is de-energized, the armature disk rests on the lining carrier with the braking force. An advantage of this is that the brake can release and engage quickly.

[0025] In a further advantageous embodiment, the tubular brake housing part is elastically deformed at a first axial end region and clamped to the brake shield at a second axial end region, also elastically deformed. The advantage of this is that the brake housing part is easy to mount and is securely held in its end position.

[0026] In a further advantageous embodiment, the pad carrier comprises two metal discs, preferably made of aluminum, which are connected to each other and separated by a damping material, and the brake pad is arranged on the pad carrier. An advantage of this is that the aluminum is recyclable and the noise generated when the brakes are applied is reduced.

[0027] In a further advantageous embodiment, the brake pad carrier and the brake lining are manufactured as a single piece from a single material. The advantages of this design are that the brake is inexpensive and easy to manufacture, and the brake lining is optimally and rotationally fixed to the brake pad carrier.

[0028] In a further advantageous embodiment, the brake is pre-assembled. The advantage here is that the electric motor is simple and inexpensive to manufacture. Furthermore, the brake is easier to replace, and different brakes can be pre-assembled for a single motor.

[0029] Important steps of the invention in the method for manufacturing an electromagnetically actuated brake for an electric motor, wherein the brake has a lining area and a magnet body, are the placing of a tubular brake housing part over the magnet body and the closing of the lining area to form a housing.

[0030] The advantage here is that the brake is easy and inexpensive to manufacture, and the abrasion from a brake pad remains in the pad area.

[0031] In a further advantageous embodiment of the method, a coil and a helical compression spring are inserted into the magnet body. The advantage here is that the brake can be controlled very dynamically and the braking force can be regulated by the type and number of helical compression springs used.

[0032] In a further advantageous embodiment of the method, the magnet body is attached to a brake plate by means of brake mounting screws, wherein an armature disc and a lining carrier are held between the magnet body and the brake plate in a lining area, the helical compression springs pressing against the armature disc and the armature disc pressing the lining carrier against the brake plate. An advantage of this is that the brake can be pre-assembled and stored and transported without additional aids.

[0033] In a further advantageous embodiment of the method, a release lever is attached to the armature disc by means of a release pin screw guided through an opening in the magnet body, the release lever supporting its bearing point on the side of the magnet body facing away from the brake shield. An advantage of this is that the brake can also be released manually.

[0034] Further advantages arise from the dependent claims. The invention is not limited to the combination of features of the claims. For those skilled in the art, further meaningful combinations of claims and / or individual claim features and / or features of the description and / or the figures will become apparent, in particular from the problem statement and / or the problem arising from a comparison with the prior art. Reference symbol list 1 Rotor 2 snap rings 3 Key 4 more keyways 5 Flattening in the wave cross-section 7 flange 8 flange bore 9 locking screw 10 retaining ring 11 fixed camps 12 retaining ring for bore 13 Cylinder screw 16 Stator 18 Stator lamination stack 20 Stator winding 21 winding head 22 more hexagon screws 32 additional retaining rings 35 Fan hood 36 fan wheel 38 fan blades 41 Spring element 42 Storage sign 44 Lotlager 46 bracket 50 electric motor 51 hand levers 52 Stator housings 53 Air lever 54 cooling fins 55 trapezoidal bulge 56 Air pin screw 57 Conical spring 58 adjusting nut 59 Cylinder pin 60 mounting holes 62 Retaining ring for drive pin 64 Flange plate 66 wave 67 Junction box bases 68 almond-shaped thickenings 70 drivers 71 Keyway 72 Rotor package 74 Rotor lamination package 76 Rotor casting 80 Fasteners 81 Slotted hole 90 footplate 93 screw 95 Brake seal ring 96 reduction 100 Hex nuts 103 Stud bolt 106 Shaft seal 107 Splash guard 108 Type plate 109 notched nail 110 Junction box 111 Seal for the junction box base 112 Junction box base 113 more screws 115 terminal plate 116 clamping brackets 117 Clamping screw 118 Spring washer 119 Fastening screw 123 Hex bolt 128 clamping brackets 128a Clamping bracket for external connection 129 Sealing screw with O-ring 131 Seal for the junction box cover 132 Junction box cover 134 Sealing screw with O-ring 136 Brake connection part 137 Brake connection part screw 139 External connection screw 140 External connection spring ring 148 External terminal clamps 149 Anchor disc 153 terminal strip 154 magnetic bodies 155 coil 156 Information sign 160 Brake mounting screw 161 Brake mounting nut 162 Cable protection 166 Brake housing part 169 Brake pad 168 decking carriers 217 Brake relay 262 Connection terminal 392 Housing seal 550 brake 615 additional connecting terminals 616 Mounting plate 702 Brake shield 705 Protective roof 706 spacers 707 Protective roof screw 718 Damping plate 900 Brake mounting screw 901 Brake seal

[0035] The invention will now be explained in more detail with the help of illustrations: In the Fig. Figure 1 shows a perspective view of an electric motor 50 according to the invention. The electric motor 50 has an approximately cylindrical stator housing 52 with cooling fins 54 arranged parallel to each other and projecting approximately radially from the stator housing. The free ends of the cooling fins 54 lie in a flat contact surface, in particular in four flat contact surfaces arranged approximately at right angles to each other. Trapezoidal ridges 55 at the end faces of the outer surfaces of the stator housing 52 form corner elements between the flat contact surfaces. In at least one of the flat contact surfaces, blind-hole-like mounting holes 60 with internal threads are provided in four almond-shaped thickenings 68 of the cooling fins 54. These serve as mounting points for various attachments, such as a base plate 90, which in turn serves to mount the electric motor 50 in different positions.

[0036] A cuboid terminal box 110 is screwed onto a terminal box base 67 provided for this purpose. The terminal box base 67 is formed integrally with the stator housing 52 and projects along the cooling fins 54 in an approximately radial direction beyond the free ends of the cooling fins 54. The terminal box 110 has a terminal box base 112 and a terminal box cover 132, which is screwed to the terminal box base 112 by means of a hexagon screw 123.

[0037] The end faces of the stator housing 52 are closed by further housing parts, such as a bearing shield 42 and a flange shield 64 – except for a passage for a shaft 66 in the flange shield 64 and a shaft passage in the bearing shield 42. A flange 7 for attaching driven devices is integrally formed on the flange shield 64. For this purpose, the flange 7 has a flange bore 8.

[0038] A socket head cap screw 13 is guided through bores in the bearing shield 42 and bores in the trapezoidal ridges 55 on the stator housing 52 and screwed into an internal thread of a bore in a trapezoidal ridge on the flange shield 64. In this way, the flange shield 64 and the bearing shield 42 are pressed against the end faces of the stator housing 52 in a rotationally fixed manner. The housing of the electric motor 50 comprises the flange shield 64, the bearing shield 42, and the stator housing 52. A clamp 46 is attached to the socket head cap screw, projecting radially outwards.

[0039] A fan hood 35 is attached to the circumference of the bearing shield 42, or partially overlapped with the bearing shield 42 in the axial direction and fastened to the bearing shield 42 with further hexagon screws 22.

[0040] Fig. 2 shows the one in Fig. 1 shown in an exploded view of the electric motor 50 according to the invention, wherein the flange shield 64 is designed as a gear flange and the electric motor 50 is additionally provided with a protective roof 705.

[0041] The rotor 1 has a shaft 66 and a rotor assembly 72, which is fixed to the shaft 66 in a rotationally fixed manner, in particular by frictional locking. The shaft 66 has several shaft sections with different diameters in the axial direction. Due to the different diameters, the transitions between the shaft sections form several shaft diameter steps. The rotor assembly 72 is arranged approximately centrally on the shaft 66 in the shaft section with the largest shaft diameter and is fixed to this shaft section in a rotationally fixed manner, in particular by being pressed onto this shaft section.

[0042] A fixed bearing 11, designed as a deep groove ball bearing, is mounted on the flange end of the shaft 66, and an inner ring of the fixed bearing 11 is axially fixed to the shaft end by a retaining ring 10 and a shaft diameter step. On the end shield side, a floating bearing 44, also designed as a deep groove ball bearing, is mounted on the shaft 66 up to a further shaft diameter step. A spring element 41 is designed as an annular spring element and, in a particularly preferred embodiment, has, in plan view from the axial direction, an approximately cloverleaf-shaped inner edge and a corresponding outer edge. "Cloverleaf-shaped" here refers to the outline of a four-leaf clover without a stem, or, in other words, a circle that is symmetrically indented inwards at four points. To generate the spring effect, the spring element 41 is, for example, corrugated in the direction of rotation.The floating bearing 44 is axially fixed in a bearing receptacle in the bearing shield 42 between the further shaft diameter step and the spring element 41. It is movable in the sense that the floating bearing 44 can follow axial displacements of the further shaft diameter step due to changes in the length of the shaft 66, since the spring element 41 springs accordingly without deforming the floating bearing 44 or adversely altering its bearing properties. In this way, for example, thermally induced changes in the length of the shaft 66 or manufacturing tolerances of the shaft 66 and the bearing receptacle are accommodated.

[0043] A driver 70 is connected to the shaft 66 in a rotationally fixed manner, for example by frictional locking and / or, in particular, by positive locking, by a driver key 71, which can be inserted into a corresponding keyway in the shaft 66. Axially, the driver 70 lies between the floating bearing 42, or the spring element 41, and a retaining ring 62 for the driver 70. The driver 70 is designed as a cylindrical gear, wherein a gear ring is divided by a circumferential groove into a bearing-end-side gear ring section and a brake-side gear ring section.

[0044] In a bearing shield-side end section of the shaft 66, a fan wheel 36 is rotationally fixed to the shaft 66, in particular by positive locking, for example with a flat 5 in the shaft cross-section or a fan wheel key. In the axial direction, the fan wheel 36 is positively and / or frictionally fixed by an additional shaft diameter step and a further retaining ring 32.

[0045] An interior of the housing is protected from contaminants such as dust, water, and / or gear oil by a splash guard 107 and a shaft seal 106 in the opening for the shaft 66 in the flange shield 64. A driven device can be flanged to the flange 7 using stud bolts 103 and hexagon nuts 100. A rotating part of this driven device can be fixed to the shaft 66 in a rotationally fixed manner, in particular by means of the key 3.

[0046] In the illustrated embodiment, the flange plate is designed as a gearbox flange plate, and a sealing screw 9 serves to close an oil inlet opening. If a gearbox is directly flanged to the flange 7, the gearbox oil can be supplied or exchanged via this oil inlet opening.

[0047] The fixed bearing 11 is fixed on the stator housing side by the flange shield 64 and a retaining ring 12 for bores.

[0048] A stator 16 has a stator lamination stack 18. A stator winding 20 is wound in the stator lamination stack 18, and a winding head 21 protrudes from the end faces of the stator lamination stack 18. The stator 16 is mounted in the stator housing 52.

[0049] The base plate 90 is attached to the stator housing 52 with screws 93.

[0050] A terminal plate 115 is attached to the terminal box base 67 by means of a further screw 113. The terminal plate 115 has at least one threaded rod designed as a connecting bolt with a nut and washer attached to the threaded rod. In the stator housing 52, in the area of ​​the terminal box base 67, there are cable glands for intended connecting leads, such as connecting leads for the stator winding 20. An inner corner of the terminal box base 67 is reinforced in an approximately cylindrical shape. This reinforcement contains a blind hole with an internal thread. Fastening screws 119, screwed into this internal thread and guided through recesses in the terminal box lower part 112, fix the terminal box lower part 112 to the terminal box base 67.Cable glands of various sizes are located in a wall of the junction box base 112. These glands can be closed using appropriately sized sealing screws 129 and 134 with O-rings. Alternatively, a brake relay 217 can be screwed into such a cable gland using a reducer 96. Its connecting cables extend into the junction box 110. The brake relay is used to control a brake 550 for the electric motor 50. Other components, such as cable clamps or rectifiers, can also be screwed into the cable glands.

[0051] The terminal box base 112 projects beyond the terminal box base 67 and the bearing plate 42 on the bearing plate side within a terminal box area, forming a base plate in this area. Various terminal devices, in particular a terminal strip 153, are located on this base plate, projecting into the interior of the terminal box base 112. The terminal strip 153 is screwed to the base plate of the terminal box base 112 using brake connection screws 137. Furthermore, a brake connection component 136, such as a brake guard, brake rectifier, and / or brake control unit, can be integrated into the terminal strip.

[0052] Towards the terminal box base 67, the terminal box lower part 112 forms a frame corresponding to the end face of the terminal box base. A seal 111 for the terminal box lower part 112 is clamped between the frame of the terminal box lower part 112 and the end face of the terminal box base 67. Through holes for fastening screws 119 are located in the four corners of the frame for attaching the terminal box lower part 112 to the terminal box base 67. Simultaneously, a mounting plate 616 with a connecting clamp 262 and / or another connecting clamp 615 can also be attached to the terminal box lower part 112 in the terminal box 110 by means of the fastening screws 119.An external connection terminal with an external connection screw 139, an external connection spring ring 140, an external connection clamping bracket 148 and a clamping bracket 128a for the external connection, such as an earthing, is attached to an outer wall of the terminal box base 112.

[0053] The terminal plate 115 and the various clamping devices are used for the electrical connection of externally supplied lines to the lines supplied from the electric motor 50 into the terminal box 110, such as the lines supplied from the stator winding 20. The clamping devices are designed, for example, as a connecting terminal 262 or as a clamping device with a clamping screw 117, a spring washer 118, and at least one clamping bracket 116. In the latter example, the clamping screw 117 is screwed into a corresponding cuboid-shaped projection on the base plate of the terminal box lower part 112, which projects into the terminal box 110. A warning label 156 is located inside the terminal box 110. The terminal box 110 is closed with a terminal box cover 132 and a seal 131 for the terminal box cover 132, which is clamped between the terminal box cover 132 and the terminal box lower part 112.For this purpose, the terminal box cover 132 is screwed to the terminal box base 112 with a hexagon screw 123.

[0054] A nameplate 108 is attached to a flat mounting surface by means of a notched nail 109. The nameplate 108 bears the technically relevant parameters as well as the product designation for the electric motor 50.

[0055] A housing seal 392 is arranged between the bearing shield 42 and the stator housing 52, which is held in a rotationally fixed position by the cylinder screws 13 via corresponding holes in the housing seal 392 and is clamped between the bearing shield 42 and the stator housing 52 in the assembled state.

[0056] For stiffening, the bearing shield 42 has radially outward-extending struts on the side facing the stator housing 52. The bearing shield 42 forms a thickening in the area of ​​the shaft passage. This thickening is shaped towards the stator housing 52. A hollow cylinder in the thickening of the bearing shield 42, which is completely open towards the stator housing, is shaped concentrically with a larger diameter than the shaft passage and forms a cylindrical bearing receptacle for the floating bearing 44. Since an outer ring and inner ring of the fixed bearing 11 are axially fixed, the floating bearing 44 does not have to absorb any axial forces acting on the shaft 66 from the outside. A thickened outer edge of the bearing shield 42 is also shaped towards the stator housing 52 and has additional cooling fins on its outer edge, which are at least partially designed as a continuation of the cooling fins 54 of the stator housing 52.A thickening is also formed on the outer edge of the bearing shield 42, which has a through bore aligned parallel to the shaft 66 and a blind hole with internal thread arranged perpendicular to it and extending radially to the shaft 66. The through bore serves to receive the socket head cap screw 13 and the blind hole with internal thread extending radially to the shaft 66 for fastening the additional hexagon head screws 22.

[0057] A brake 550 is screwed to the bearing plate 42 using brake mounting screws 900. The brake 550 comprises a brake shield 702, a lining carrier 168, an approximately tubular brake housing part 166, and a magnet body 154, as well as other parts, which are assembled using a brake mounting screw 160 and a brake mounting nut 161. This assembly takes place before the brake 550 is installed. It is therefore a pre-assembled brake. The pre-assembled brake is placed completely onto the drive 70 or onto the shaft 66, whereby the pre-assembled brake is first engaged and then screwed into place by gently rotating the shaft 66 or the pre-assembled brake back and forth.

[0058] The approximately tubular brake housing part 166 is made of an elastic material, preferably elastic rubber or silicone. The approximately cylindrical disc-shaped brake 550 is arranged around the shaft 66 between the bearing shield 42 and the fan wheel 36. A brake seal 901 is clamped between the bearing shield 42 and the brake 550. The brake seal 901 is approximately identical in shape to an end face of an outer circumference of the brake shield 702. The disc-shaped brake shield 702, which is provided with radial, star-shaped reinforcements, has a smaller outer diameter than the bearing shield 42. Trapezoidal protrusions with axial through-holes are formed on the circumferential region of the brake shield 702 that faces the bearing shield 42; the brake mounting screws 900 are guided through these protrusions. The brake seal 901 has analogous through-openings to clamp the brake seal 901 in a rotationally defined position between the bearing shield and the brake shield 702.

[0059] The lining carrier 168 has internal teeth which engage axially in a toothing of the fan-side toothed ring section of the impeller 70. The lining carrier 168 is arranged between the brake shield 702 and the magnet body 154 and lies in a lining area that is bounded by the brake shield 702, the magnet body 154 and the approximately tubular brake housing part 166.

[0060] A coil 155 is arranged in the magnetic body 154. A cable for controlling the coil is routed from the terminal box 110 through a hose-like cable guard 162, through the housing, under the sealing strip 166, to the magnetic body 154. The approximately cylindrical disc-shaped magnetic body 154 has notches on its outer edge, on the side facing away from the brake shield. These notches interrupt a circumferential corner between the outer wall and the end face, forming triangular side walls. An annular opening between the shaft 66 and the magnetic body 154 is sealed with a brake seal 95. The brake seal 95 is shaped as a hollow cylinder with a circumferential, radially projecting disc. A continuous recess is located in the circumferential, radially projecting disc, in which a cylindrical pin 59 is arranged. One of the end faces of the cylindrical pin 59 rests against the magnetic body 154.

[0061] A release lever 53 for releasing the brake 550 rests on the cylindrical pin 59 with a cuboid-shaped recess in one end region of the release lever 53 and is arranged on the end face of the magnet body 154 facing away from the brake shield. In axial plan view, the release lever 53 is approximately pear-shaped. At its widest point, a central through-hole for the passage of the shaft 66 is machined, which is surrounded by two smaller, opposing through-holes. A release pin screw 56 passes through one of the smaller through-holes, a corresponding opening in the disc of the brake seal 95, and the magnet body 154, and is screwed with a threaded end region onto an armature disk 149 of the brake 550, which is arranged between the magnet body 154 and the lining carrier 168.The air release lever 53 is fixed to the other end of the air release screw 56 by means of a conical spring 57 and an adjusting nut 58 and is supported against the end face of the magnet body 154. The other end of the air release lever 53 is bent towards the magnet body 154 and, in the assembled state, rests in the notch of the magnet body. The bent end has a through-hole with an internal thread in the radial direction for screwing in a hand lever 51. In the assembled state, the hand lever projects radially away from the shaft 66 and is rigidly connected to the air release lever 53.

[0062] The fan wheel 36 is positioned between the fan lever 53 and the grille structure of the fan cover 35 in the assembled state and is enclosed by the fan cover 35.

[0063] The fan housing 35 has the shape of an approximately rectangular shell with rounded corners and a flat base, the base of which is not closed but formed by a grid structure. The fan housing 35 is slid onto the bearing shield 42 with its opening facing the bearing shield 42, so that the grid structure of the fan housing runs approximately parallel to the bearing shield 42. A circumferential wall of the fan housing 35 has a first section extending parallel to the axial direction of the shaft 66 and a second section running inwards in a funnel shape at an angle to the axial direction of the shaft 66. The first section has a first subsection on the stator housing side with a corresponding circumference suitable for partially overlapping and fitting onto the bearing shield 42. A second subsection adjoining this, in the direction of the grid structure, has a circumference reduced by a step.In wall sections at the rounded corners, L-shaped recesses are arranged on the stator housing side. These allow the fan cover 35 to be inserted into the additional hexagonal screws 22, which are screwed to the bearing plate 42. The fan cover 35 is then secured to the bearing plate 42 by finally tightening these additional hexagonal screws 22. Further C-shaped recesses extend around the L-shaped recesses and reduce the transmission of vibrations from the electric motor 50 to the fan cover 35. The elongated hole 81 is located in the second subsection of the first subsection and is positioned such that the hand lever 51, attached to the release lever 53, protrudes from the elongated hole 81, allowing the brake 550 to be released manually.

[0064] The second section of the fan hood 35 has approximately wave-shaped elevations and depressions in the sections which, in the assembled state, are designed as a continuation of the flat bearing surfaces of the stator housing 52.

[0065] A saucer-shaped protective cover 705 is arranged to cover the grid structure of the fan housing 35. A spacer 706 is arranged between the protective cover 705 and the fan housing 35, ensuring that sufficient air can flow through the grid structure to the fan wheel 36. The protective cover 705 and the spacer 706 have through holes through which a protective cover screw 707 passes. In the assembled state, the protective cover screw 707 is screwed into threads arranged on the fan housing 35. Thus, the protective cover 705 and the spacer 706 are fastened to the fan housing 35. An additional key 4 on a fan-side end region of the shaft 66 serves for a rotationally fixed, positive-locking connection of additional devices to the shaft 66.

[0066] Fig. 3 shows the one in Fig. 1 shown electric motor 50 according to the invention in a longitudinal section.

[0067] The flange shield 64 and the bearing shield 42, together with the stator housing 52, enclose the approximately cylindrical interior of the housing. The shaft 66 is supported relative to the housing by the fixed bearing 11 and the floating bearing 44. The fixed bearing 11 is arranged in a fixed bearing holder formed in the flange shield 64 and is held on the shaft side by the shaft diameter step and the retaining ring 10. The retaining ring 10 snaps into an annular groove in the shaft 66. On the housing side, the fixed bearing 11 is held by an annular corner of the fixed bearing holder and by the retaining ring for a bore 12. The retaining ring for a bore 12 engages in a groove in the fixed bearing holder in the flange shield 64. The remaining opening of the shaft passage in the flange shield 64 is sealed by the shaft seal 106.

[0068] The stator 16, comprising the stator windings 20 with winding head 21 and the stator lamination stack 18, is fixed in the stator housing 52 by means of fasteners 80, in particular by being pressed into the stator housing 52. The rotor stack 72, pressed onto the shaft 66, has a rotor lamination stack 74. The laminations of the rotor lamination stack 74 are connected to one another, for example by stamping and / or by a rotor casting 76, which forms a squirrel cage for the rotor 1. The rotor casting 76, forming an annular ridge, projects axially from both sides of the rotor lamination stack 74 in the direction of the shaft 66.

[0069] The floating bearing 44 is arranged in the cylindrical bearing receptacle. The inner ring of the floating bearing 44, with its stator housing-side end face abutting a radial surface of a further shaft diameter step, provides shaft-side support to the rotor assembly 72. The spring element 41 is arranged between the floating bearing 44 and the bearing shield 42 in the cylindrical bearing receptacle and rests on a support surface in the bearing shield. The outer ring diameter of the spring element 41 is larger than the diameter of the shaft passage and less than or equal to the diameter of the cylindrical bearing receptacle. The inner opening diameter of the annular spring element 41 is at least as large as the shaft diameter of the shaft 66 in the region of the cylindrical bearing receptacle.Due to the special circumferentially corrugated shape of the annular spring element 41, the spring element 41 does not completely circumferentially contact the end face of an outer ring of the floating bearing 44 on the bearing shield side, but does so at least along a section. On the bearing shield side, the spring element 41 contacts the bearing shield 42 at least along another section of the support surface. This support surface only needs to absorb one spring force of the spring element in the axial direction. For example, in the special design as a cloverleaf-shaped spring element 41, the inwardly extended sections with the smaller outer diameter contact the bearing shield 42, and the outwardly extended sections with the maximum outer diameter of the compensating washer contact the outer ring of the floating bearing.When the shaft 66 undergoes an axial change in length, the floating bearing 44 follows the movement of the shaft diameter step and the inner ring of the floating bearing 44 remains pressed against the radial surface of the shaft diameter step due to the spring force of the spring element 41.

[0070] The inner ring of the floating bearing 44 is axially fixed by the further shaft diameter step and the driver 70. Therefore, the spring element 41 can also be omitted. The driver 70, in turn, is axially fixed by the retaining ring 62 for the driver 70, which is engaged in a circumferential annular groove of the shaft 66. The toothed ring section of the driver 70 on the bearing shield side lies within the shaft passage of the bearing shield 42.

[0071] The brake shield 702 is attached to the bearing shield 42. The circumferential area shaped towards the bearing shield 42 includes an annular protrusion on the end face of the bearing shield 42 located outside the housing, which approximately centers the brake shield 702 around the shaft 66. This facilitates the assembly of the brake shield 702 and thus of the pre-assembled brake 550. A disc-like portion of the end face of the brake shield 702 facing the magnet body serves as a friction surface for an annular brake pad 169 of the pad carrier 168.

[0072] The brake pad carrier 168 comprises two metal discs, preferably made of aluminum, which are connected to each other and separated by a damping material. The damping material reduces the noise generated when the brake 550 is applied. The annular brake pad 169 is arranged on the metal disc facing the brake shield 702. Another brake pad is arranged on the opposite metal disc facing the magnet body 154. The internal teeth of the brake pad carrier 168 engage axially movably with the external teeth of the driver 70. Blind holes, open towards the brake pad carrier and arranged axially in the magnet body 154, are provided.In these blind holes in the magnet body 154, helical compression springs are inserted which, when the brake 550 is applied, press the anchor disc 149 against the pad carrier 168 or the further brake pad, whereby the brake pad 169 presses against the disc-like part of the end face of the brake shield 702 due to the axial mobility of the pad carrier 168.

[0073] A coil 155 is arranged in the magnet body 154. When current flows through the coil 155, it magnetizes the magnet body 154, thereby attracting the armature disk 149 against the force of the helical compression springs. When current flows through the coil 155, the brake 550 is released, and the shaft 66 can be driven without braking, i.e., it is movable. To dampen the noise generated when the armature disk 149 strikes the magnet body 154, a disc-shaped damping plate 718 is arranged between the magnet body 154 and the armature disk 149.

[0074] The lining area between the brake shield 702 and the magnet body 154 is closed off by the approximately tubular brake housing part 166. The tubular brake housing part is so elastic that, although it has a smaller inner diameter than the outer diameter of the magnet body 154, it can be slipped over the magnet body.

[0075] The elastic material of the tubular brake housing part 166 has a lower thermal conductivity than, for example, steel. When the brake 550 is released, heat is generated in the magnet body 154 due to the current-carrying coil and the magnetic field. Due to the inventive design of the tubular brake housing part 166, this heat is not transferred via the tubular brake housing part 166 to the brake shield 702 and thus to the housing of the electric motor. The electric motor is not burdened by the additional heat generated in the magnet body 154 and can be operated more efficiently. The approximately tubular brake housing part 166 is so elastic that it can be slipped over the magnet body 154 against the brake shield 702. This simplifies the assembly of the brake 550.In the assembled state, the approximately tubular brake housing part 166 rests with one end region on the protrusion on the pad carrier-side end face of the brake shield 702 and with the opposite end region on the magnet body 154.

[0076] In addition, the nearly tubular brake housing part 166 prevents abrasion from the pad carrier 168 or the brake pad 169 from being distributed uncontrollably or even being caught by the airflow generated by the fan wheel 36 when the motor is rotating and transported towards the electric motor 50. There, the abrasion could accumulate on the cooling fins and prevent efficient cooling of the electric motor 50.

[0077] Another advantage of the tubular brake housing part 166 is the damping of airborne and structure-borne noise, which is caused by the movement of the armature disc 149, or by the impact of the armature disc 149 on the brake pad or on the magnet body 154 when the brake 550 engages and disengages.

[0078] Towards the bottom of the fan shroud 35, the remaining opening between the magnet body 154 and the shaft 66 is sealed by the brake seal 95. Following the brake seal 95 in an axial direction away from the housing is the air lever 53, which rests on the end face of the magnet body 154 facing away from the housing, as it is fastened to the armature disk 149 by means of the air pin screw 56 and the adjusting nut 58.

[0079] The fan wheel 36 is arranged between the grid structure and the air lever 53, spaced apart from the air lever 53, and is rotationally fixed, for example by a positive fit through a flattened section in the shaft cross-section 5 and / or by a friction fit to the shaft 66. The fan wheel 36 is axially fixed by the additional shaft diameter step in the shaft 66 and the further retaining ring 32. The fan wheel 36 has a radially projecting fan disc forming a truncated cone shell, open at its base towards the bearing shield 42.

[0080] A radially extending fan blade 38 is positioned on the side of the fan disc facing away from the housing, approximately perpendicular to the fan disc. The fan disc transitions radially towards the shaft 66 into a U-shaped mounting area 37 of the fan wheel 36. An innermost edge of the mounting area 37 forms the inner surface of a fan wheel cylinder that is in contact with the shaft 66. The shaft-side leg of the U of the mounting area is clamped by the further shaft diameter step of the shaft 66 and the further retaining ring 32. Thus, the fan wheel 36 is secured in the axial direction.

[0081] A sealing area forming two lips 39 is formed around the mounting area 37. The two lips 39 face the magnet body 154. The fan cover 35 conceals the fan wheel 36, the air lever 53, the brake 550, the bearing shield 42, and one end of the shaft 66 at the bearing shield end. The fan wheel 36 is preferably molded or injection-molded in one piece from a lightweight material such as plastic or aluminum. To increase the inertia of the drive shaft, it may also be advantageous in certain applications to manufacture the fan wheel from steel or cast iron.

[0082] Blind holes in the end faces of the shaft 66 and a snap ring 2 serve as further centering and / or fastening options for various elements to be driven.

Claims

[1] Electric motor (50) comprising a housing, a stator (16), a rotor (1) and a brake (550), wherein the housing comprises a flange shield (64), a stator housing (52) and a bearing shield (42), wherein the rotor (1) comprises a rotor assembly (72) and a shaft (66) which has sections of different diameters separated by shaft diameter steps, wherein the brake (550) comprises an armature disk (149), a magnet body (154) with coil (155) and a lining carrier (168) which is non-rotatably connected to the shaft (66) by means of a driver (70), wherein a brake pad (169) arranged in a pad area is arranged in a pad area and an approximately tubular brake housing part (166) surrounds the pad area in a housing-forming manner, wherein the brake pad (169) is arranged on the pad carrier (168), wherein an inner ring of a floating bearing (44) is fixed on the shaft side in an axial direction by a further shaft diameter step and the driver (70), wherein a lifting lever (53) is supported at its bearing point on the magnet body (154), the lifting lever (53) is connected to the armature disk (149) via a lifting pin screw (56) and the armature disk (149) can be pressed against the magnet body (154) by means of a hand lever (51) which protrudes radially from the electric motor (50) to the shaft (66) and is rigidly connected to the lifting lever (53), wherein a fan wheel (36) is non-rotatably connected to the shaft (36) and wherein the brake (550) and the fan wheel (36) are surrounded by a fan cover (35) forming a housing, wherein the tubular brake housing part (166) is elastically deformed at a first axial end region and is elastically deformed at a second axial end region and is clamped on the magnet body (154), wherein the air lever (53) supports its contact point on the side of the magnet body (154) facing away from the brake shield (702). [2] Electric motor according to claim 1, wherein the flange shield is designed as a gearbox flange shield and an oil inlet opening can be closed by a sealing screw (9). [3] Electromagnetically actuated brake (550) for an electric motor (50) according to claim 1 or 2, wherein the brake (550) comprises a brake lining (169) arranged in a lining area and a magnetic body (154), characterized by , that a tubular brake housing part (166) made of such an elastic material that it can be slipped over the magnet body and the tubular brake housing part (166) surrounds the pad area, forming a housing. [4] Brake according to claim 3, characterized by , that the tubular brake housing part (166) is made of an elastic material which conducts heat less efficiently than a metal or stainless steel. [5] Brake according to claim 4, characterized by that the elastic material is an elastic rubber. [6] Brake (550) according to one of claims 3 to 4, characterized by , that the brake (550) is connected in a rotationally fixed manner to a shaft (66) of the electric motor (50), the brake pad (169) comprising a pad carrier (168), an axially movable and essentially rotationally fixed armature disk (149) and the magnet body (154) comprising a coil (155). [7] Brake (550) according to claim 6, characterized by , that the lining carrier (168) and the armature disk (149) which can be attracted by the magnet body (154) when the coil (155) is energized against a brake pressure force applied by helical compression springs are arranged in the lining area between the magnet body (154) and the brake shield (702) and when the coil (155) is de-energized the armature disk (149) rests on the lining carrier (168) with the brake pressure force. [8] Brake (550) according to one of claims 6 to 7, characterized by , that the pad carrier (168) comprises two metal discs which are connected to each other, separated by a damping material, and the brake pad (169) is arranged on the pad carrier (168). [9] Brake according to claim 9, characterized by that the metal discs are made of aluminum. [10] Brake (550) according to any one of claims 6 to 8, characterized by, that the pad carrier (168) and a brake pad (169) are made in one piece and consist of a single material. [11] Brake (550) according to any one of claims 3 to 10, characterized by , that the brake (550) is pre-assembled. [12] Method for manufacturing an electromagnetically actuated brake (550) for an electric motor (50) according to claim 1, wherein the brake has a lining area and a magnetic body (154), comprising the following steps: - Placing an approximately hose-shaped brake housing part (166) over the magnet body (154) and closing the pad area to form a housing. [13] Method for manufacturing an electromagnetically actuated brake (550) according to claim 12, comprising the following steps: - Inserting a coil (155) and a helical compression spring into a magnetic body (154). [14] Method for manufacturing an electromagnetically actuated brake (550) according to claim 12 or 13, comprising the following steps: - Attaching the magnet body (154) to a brake shield (702) by means of brake mounting screws, wherein an anchor disc (149) and a lining carrier (168) are held between the magnet body (154) and the brake shield (702) in a lining area, wherein the screw compression springs press against the anchor disc (149) and the anchor disc (149) presses the lining carrier (168) against the brake shield. [15] Method for manufacturing an electromagnetically actuated brake (550) according to any one of claims 12 to 14, comprising the following steps: - Attaching a vent lever (53) to the armature disk (149) by means of a vent pin screw (56) guided through an opening in the magnet body (154), wherein the vent lever (53) supports its bearing point on the side of the magnet body (154) facing away from the brake shield (702).

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