CN116691906A - Drive assembly and vehicle - Google Patents
Drive assembly and vehicle Download PDFInfo
- Publication number
- CN116691906A CN116691906A CN202310188166.XA CN202310188166A CN116691906A CN 116691906 A CN116691906 A CN 116691906A CN 202310188166 A CN202310188166 A CN 202310188166A CN 116691906 A CN116691906 A CN 116691906A
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- Prior art keywords
- wall
- drive assembly
- assembly according
- bolt
- flange
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- 210000003205 muscle Anatomy 0.000 claims abstract description 7
- 238000013016 damping Methods 0.000 claims description 86
- 238000007789 sealing Methods 0.000 claims description 44
- 239000000463 material Substances 0.000 claims description 13
- 230000006835 compression Effects 0.000 claims description 10
- 238000007906 compression Methods 0.000 claims description 10
- 230000005489 elastic deformation Effects 0.000 claims description 3
- 238000005553 drilling Methods 0.000 claims 2
- 239000011358 absorbing material Substances 0.000 claims 1
- 238000009434 installation Methods 0.000 description 10
- 230000005540 biological transmission Effects 0.000 description 9
- 230000004323 axial length Effects 0.000 description 8
- 230000000694 effects Effects 0.000 description 8
- 229910000831 Steel Inorganic materials 0.000 description 6
- 239000010959 steel Substances 0.000 description 6
- 229920001971 elastomer Polymers 0.000 description 5
- 239000004033 plastic Substances 0.000 description 5
- 229920003023 plastic Polymers 0.000 description 5
- 229910052782 aluminium Inorganic materials 0.000 description 4
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 4
- 239000011324 bead Substances 0.000 description 4
- 239000000806 elastomer Substances 0.000 description 4
- 239000012530 fluid Substances 0.000 description 4
- 238000003780 insertion Methods 0.000 description 4
- 230000037431 insertion Effects 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 4
- FYYHWMGAXLPEAU-UHFFFAOYSA-N Magnesium Chemical compound [Mg] FYYHWMGAXLPEAU-UHFFFAOYSA-N 0.000 description 3
- 230000006978 adaptation Effects 0.000 description 3
- 238000010276 construction Methods 0.000 description 3
- 238000007667 floating Methods 0.000 description 3
- 239000011777 magnesium Substances 0.000 description 3
- 229910052749 magnesium Inorganic materials 0.000 description 3
- 230000008719 thickening Effects 0.000 description 3
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 2
- 229910000760 Hardened steel Inorganic materials 0.000 description 2
- 229910052799 carbon Inorganic materials 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 230000000254 damaging effect Effects 0.000 description 2
- 230000014759 maintenance of location Effects 0.000 description 2
- 230000010355 oscillation Effects 0.000 description 2
- 230000035515 penetration Effects 0.000 description 2
- 238000009420 retrofitting Methods 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 239000004411 aluminium Substances 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000004918 carbon fiber reinforced polymer Substances 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 239000013013 elastic material Substances 0.000 description 1
- 238000006056 electrooxidation reaction Methods 0.000 description 1
- 239000000835 fiber Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 238000012958 reprocessing Methods 0.000 description 1
- 239000011343 solid material Substances 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
- B62M6/00—Rider propulsion of wheeled vehicles with additional source of power, e.g. combustion engine or electric motor
- B62M6/40—Rider propelled cycles with auxiliary electric motor
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
- B62M6/00—Rider propulsion of wheeled vehicles with additional source of power, e.g. combustion engine or electric motor
- B62M6/80—Accessories, e.g. power sources; Arrangements thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
- F03G5/00—Devices for producing mechanical power from muscle energy
- F03G5/06—Devices for producing mechanical power from muscle energy other than of endless-walk type
- F03G5/062—Devices for producing mechanical power from muscle energy other than of endless-walk type driven by humans
- F03G5/063—Devices for producing mechanical power from muscle energy other than of endless-walk type driven by humans operated by the leg or foot
- F03G5/064—Devices for producing mechanical power from muscle energy other than of endless-walk type driven by humans operated by the leg or foot using a bicycle or a bicycle pedal, e.g. pedal generators
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- Health & Medical Sciences (AREA)
- Toxicology (AREA)
- General Engineering & Computer Science (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The invention relates to a drive assembly (1) of a vehicle (100) that can be driven with muscle force and/or motor force, comprising a drive unit (2), a frame interface (3), two sleeves (41, 42) and a through-bolt (5), wherein the drive unit (2) is arranged at least partially between a first wall (31) and a second wall (32) of the frame interface (3), wherein the drive unit (2) has a through-bore (20), the two sleeves being inserted into the through-bore (20) of the drive unit (2) on both sides, the through-bolt being inserted through the through-bore (20) and the two sleeves (41, 42) and holding the drive unit (2) on each of the two walls (31, 32).
Description
Technical Field
The present invention relates to a drive assembly and a vehicle including the same.
Background
Drive assemblies having a drive unit held between two walls of a frame interface are known. The drive unit is screwed to the two opposing walls. In general, a gap between the drive unit and one of the walls should be bridged. In order to achieve this, for example, a retaining plate can be provided on the drive unit, which retaining plate is elastically deformed in order to bridge the gap. However, this may adversely affect the mechanical load and tightness of the drive assembly.
Disclosure of Invention
In contrast, the drive assembly according to the invention is characterized in that a technically advantageous holding of the drive unit in the housing is achieved. In addition, a particularly simple and cost-effective production and installation of the drive assembly is achieved. This is achieved by a drive assembly comprising a drive unit and a frame interface. The drive unit is at least partially disposed between the first wall and the second wall of the frame interface. Preferably, the first wall and the second wall are connected to each other by means of a connecting wall, in particular such that the first wall, the second wall and the connecting wall together form a one-piece U-shaped frame. The drive unit has a through bore. The drive assembly further comprises two sleeves which are inserted into the through-bore of the drive unit on both sides, i.e. at both ends of the through-bore, and a through-bolt which is inserted through the through-bore and the two sleeves. The through-bolts hold the drive unit on each of the two walls, in particular indirectly via the two sleeves.
In other words, a threaded connection is provided in the drive assembly, which threaded connection holds the drive unit on the frame interface in such a way that a through-bolt is threaded through the drive unit. Thereby obtaining a number of advantages. On the one hand, it is thereby possible to mount the drive assembly on the frame interface and detach it from the frame interface in a particularly simple manner. For example, the through-bolts can be actuated, i.e. for example inserted, rotated or pulled out, on the side of one of the two walls. This is particularly advantageous because of limited accessibility on the chain wheel side when applied on an electric bicycle. Accordingly, the operability of the through-bolts can be provided on the opposite side. Furthermore, a particularly robust connection, in particular in terms of lateral loads, can be achieved by using through bolts having a relatively large diameter. For example, slippage of the screw connection can thereby also be avoided. Furthermore, the desired load state of the drive unit can be optimally set by means of the sleeve. For example, a corresponding design of the sleeve can provide a neutral installation state of the drive unit in which no axial forces act on the drive unit, in particular with respect to the longitudinal axis of the through-bolt. Alternatively, the sleeve can be designed, for example, in such a way that, by clamping by means of the through-bolts, a light or strong compressive stress is induced on the drive unit in the axial direction, which can advantageously influence the tightness of the drive unit against the ingress of fluid. The sleeve also enables an advantageous distribution of the mechanical forces acting on the drive unit, in particular by an increased contact surface of the drive unit with fastening elements which hold the drive unit on the frame interface. This is particularly advantageous if the drive unit or the housing of the drive unit is formed from aluminium or magnesium. The sleeve can be formed, for example, from a harder material, for example steel. Hereby, a particularly stable fastening with reduced risk of damage of the drive unit or its housing is provided. Furthermore, the sleeve allows for a particularly simple adaptation, for example to different frame interfaces and/or to different tolerances of the frame interfaces.
The content of the preferred embodiment is a preferred extension of the present invention.
Preferably, the two sleeves are in contact with each other within the through bore. In this case, the two sleeves are clamped against one another by means of the through-bolts. As a result of the mutual contact of the sleeves in the through-bore, axial forces which may occur as a function of the fastening means on the frame interface can be received by the sleeves, so that the mechanical load of the drive unit is reduced.
Preferably, each sleeve has a stem and a flange. The rod is preferably configured as a hollow cylinder, and the flange is preferably arranged on an axial end of the rod and has a larger outer diameter than the rod. The rod is here at least partially arranged in the through-bore and the flange is arranged outside the through-bore. In particular, the flange is configured to rest on the end face of the drive unit surrounding the through-bore and to precisely define the insertion depth of the shaft of the sleeve. In this way, a desired mechanical load can be set particularly simply and precisely.
It is particularly advantageous to provide the sleeve flange with different thicknesses, in particular with respect to the axial direction of the sleeve. For example, the flange of the sleeve of the first embodiment can have a first thickness, wherein the flange of the sleeve of the second embodiment can have a second thickness that is at least 1.5 times, preferably at least twice, in particular at least three times, the first thickness. This gives the advantage that: the width of the drive assembly, preferably measured in the axial direction of the through-bore, is variable in a particularly simple and cost-effective manner. For example, the width of the drive assembly can be adapted to different width frame interfaces by varying the thickness of the sleeve flange, so that the drive assembly can be used particularly flexibly and cost-effectively.
It is particularly preferred that each sleeve has a damping element arranged on the side of the flange facing the drive unit. The damping element is formed here from a damping material. Preferably, the damping element is formed from an elastomer. The damping element forms a certain damping effect here due to the elastic deformability between the flange and the drive unit. The drive assembly can thus be designed in a simple and cost-effective manner in such a way that the drive unit is held, for example, free of play in the axial direction of the through-bore, in that the damping element is deformed or partially compressed under pressure. Additionally, the damping element can reduce vibrations and oscillations between the drive unit and the frame interface. Furthermore, the damping element advantageously causes a sealing effect between the sleeve and the drive unit.
Preferably, the damping element additionally surrounds the rod at least partially, preferably completely, in the circumferential direction. In particular, the damping element is thus configured as a collar of the rod and facing the flange side of the rod. The damping element thus provides the advantage of fastening the drive unit to the frame interface in a vibration-mechanically optimized manner. This particularly advantageously affects the durability of the screw-on, since in particular by the damping effect the transmission of vibrations and oscillations and the alternating dynamic loads are reduced due to the spring and damping properties of the damping element. Thus, the alternating mechanical load of the screw connection is also reduced or prevented, thereby enabling a high durability to be provided. Furthermore, the occurrence of undesired noise can thereby be reduced, for example. Furthermore, the damping element allows for a certain tolerance compensation. In addition, the advantage of additional corrosion protection, in particular electrochemical corrosion protection, arises, for example, when the drive unit has a housing made of magnesium, wherein the sleeve is formed, for example, from aluminum. Furthermore, an axial and radial sealing effect can be provided on the drive unit.
It is particularly preferred that the damping element has a projecting sealing bead on the axial end opposite the flange, which sealing bead projects axially and radially from the rod. In particular, the sealing projection protrudes axially and radially from the remaining region of the damping element. For example, a thickening of the damping element, which surrounds the damping element in an annular manner, is regarded as a sealing projection. In particular, on both sleeves, a protruding sealing bead is provided on the damping element, respectively. The sealing projection here provides the advantage of an improved seal against fluid ingress. In particular, the contact planes of the rods of the two sleeves which are in contact with one another in the through-bore and the radially outer part of the rods of the sleeves are thus sealed in such a way that the two sealing projections of the sleeves are compressed against one another in the axial direction. Additionally, the sealing bead is preferably designed such that radial compression with the inner periphery of the through-bore is achieved. In particular, additional sealing elements, for example O-rings, between the through-screw and the sleeve can thus be dispensed with. This gives rise to a number of advantages, for example cost savings, since no precise sealing contour is required at the inner side of the sleeve. Furthermore, the drive assembly can be installed more simply.
Preferably, the sealing projection protrudes beyond the end side of the rod opposite the flange in the axial direction. In particular, such axial projections are at least 20% of the wall thickness of the stem, so as to be able to provide a reliable compression and thus a reliable seal.
It is further preferred that the two sleeves are designed such that they are arranged relative to one another with a predefined axial distance in the through-bore hole in the fully inserted state into the through-bore hole and simultaneously in the undamped state. In other words, when the sleeve is inserted into the through-bore without clamping it, the sum of the axial lengths of the sleeve is less than the entire axial length of the through-bore.
Preferably, the predefined axial distance is designed such that in the clamped state of the two sleeves caused by the through-bolts, the axial distance is compensated for by the elastic deformation of the damping element. I.e. the sleeves are in contact with each other in the through-going bore. In other words, the two sleeves are designed such that, in the clamped state, when the two sleeves come into contact with one another in the through-bore, the respective damping element of the two sleeves is elastically deformed, in particular compressed, between the flange and the drive unit. In this way, a predetermined load state of the drive unit with a small predetermined compressive stress can be set in a particularly simple manner. Furthermore, a sealing is reliably ensured by means of the deformed or compressed damping element. As a result of the mutual contact of the sleeves, the reception of axial mechanical forces is also ensured by the sleeves, so that, for example, the screwing of the through-bolts can be effected with high torque without excessive mechanical loading of the drive unit occurring. At the same time, a particularly stable screw-on is thereby possible.
Preferably, the flange of at least one of the two sleeves has a plurality of protruding form-locking elements on the side facing the respective wall. The form-locking elements are designed such that they are pressed into the corresponding walls by screwing the sleeve onto these walls. In particular, the form-locking element causes plastic deformation of the wall by pressing it into the wall, in particular in such a way that the form-locking element and the plastic deformation region of the wall form a form-locking in a plane perpendicular to the screw axis. The sleeve has protruding form-locking elements on the surface of the flange, which form-locking elements partially embed into the wall when the sleeve and the wall are screwed to one another, in particular in order to produce a micro-form-locking in the plane of the wall surface. A particularly secure connection of the drive unit to the frame interface can thereby be provided, since slippage between the sleeve and the wall can be reliably prevented in a simple manner.
Particularly preferably, the flange of the sleeve is of two-part design and comprises a flange base and an insert ring. The flange base body is jointly formed as a one-piece component together with the shaft of the sleeve. The form-locking element is preferably arranged only on the insert ring. I.e. the insert ring with the form-locking element is provided as a separate component with respect to the rest of the sleeve. In particular, the manufacturing advantages result from this, since a significantly higher flexibility is achieved in terms of the geometry and material selection of the sleeve and the form-locking element. Preferably, the insert ring is immovably fixed to the flange base.
Preferably, the insert ring is arranged in an in particular annular groove of the flange base body. In this way, a simple and precisely defined relative arrangement of the insert ring and the flange base body is obtained for optimally positioning the form-locking element. Preferably, the insert ring is held in the groove by means of an axial form fit. In other words, at least the insert ring and a partial region of the flange base body are laterally cut in the axial direction of the sleeve in such a way that the insert ring is held securely in the groove. For example, the axial form-locking can be formed in the form of a caulking of the partial regions of the flange base body, for example by plastic deformation. Thus, a simple and cost-effective manufacture of the sleeve can be achieved.
Preferably, the flange base and the insert ring are formed of different materials. It is particularly advantageous if the insert ring has a greater hardness than the flange base. Preferably, the flange base and preferably the stem of the sleeve are formed of steel well suited for cold retrofitting. In this way, a simple and cost-effective manufacturability of the sleeve is achieved. Further preferably, the insert ring is formed of hardened steel. In this way, a particularly stable geometry of the form-locking element can be provided, as a result of which the function of the form-locking element is achieved particularly reliably.
Preferably, each of the form-locking elements has a pyramid protruding from the surface of the flange of the sleeve. Alternatively, each form-locking element has, for example, a cone protruding from the surface of the flange of the sleeve. In other words, a plurality of pyramid tips protruding from the surface of the flange are provided as form-locking elements. Particularly preferably, the pyramids are formed in sharp fashion and in particular have a taper angle of less than 60 °, preferably less than 45 °, so that they can penetrate into the wall particularly easily. Such a configuration with a pointed pyramid as a form-locking element is particularly advantageous when the drive unit is screwed onto the carbon frame, i.e. the frame interface made at least in part of a fiber-reinforced, preferably carbon fiber-reinforced plastic. Here, this advantage is obtained: sharp pyramids can be imprinted into the network without damaging the carbon network. In particular, the fibers do not break when the pyramid is immersed, but rather can be avoided and placed around the corresponding pyramid.
It is further preferred that each form-locking element has a recess in the surface of the flange adjoining the pyramid, for example surrounding the pyramid. Preferably, the recess is configured as an annular groove. Particularly preferably, a single recess is formed in the surface of the flange, on the radially inner and/or outer side of which a pyramid is arranged. Alternatively, individual recesses can be formed for each pyramid, wherein the recesses are arranged in particular next to the pyramid. The recess can receive, for example, wall material which is pressed into the wall as a result of the penetration of the pyramid, so that the surface of the flange can rest against the wall in a reliable and defined manner.
Preferably, the flange of at least one of the two sleeves has a taper on the radially outer end. Preferably, the flange is configured as a disk. The taper is arranged here on the side of the flange facing the shank. The reduction in the thickness of the flange, in particular in the axial direction of the sleeve, is considered in particular as a taper. In particular, the taper corresponds to the difference between the maximum thickness and the minimum thickness of the flange, wherein this difference preferably corresponds to at least 50%, preferably at most 150%, of the wall thickness of the stem of the sleeve. The tapering of the flange is compensated for by the damping element. In other words, the damping element thickness in the region of the taper is greater than in the remaining region of the flange. Preferably, the total thickness of the damping sleeve is constant in the axial direction in the region of the flange. Alternatively, the damping element can have a thickening on the radially outer end on the side facing the rod. By virtue of the tapering of the flange and the thicker damping element in this region, a soft region of the damping sleeve can be provided in this region, which achieves a particularly good sealing effect between the damping sleeve and the drive unit.
It is further preferred that the drive unit has at least one protruding annular rib arranged concentrically with one of the two openings. Preferably, the annular rib has a tapered or trapezoidal cross section. It is particularly preferred that the protruding annular rib and the taper of the flange of the sleeve are arranged on the same radius with respect to the opening axis of the opening of the drive unit. In other words, the protruding annular rib and the taper of the flange of the sleeve are arranged at the same height with respect to the radial direction of the opening of the drive unit. The protruding annular rib can thus optimally penetrate into the thicker region of the damping element when the drive assembly is mounted, so that a particularly good sealing effect can thereby be provided between the damping sleeve and the drive unit.
Preferably, the through-bolts are fastened to the second wall. The through-bolts clamp the two sleeves and the second wall relative to one another. In particular, the through-bolt sandwiches the two sleeves between the bolt head and the second wall. The through-bolt is held axially movably on the first wall. In particular, the through-bolt is held on the first wall in a radial direction, in particular substantially immovably, for example in that it is arranged at least partially in the through-opening of the first wall. In this way, tolerance compensation can be performed in a particularly simple manner between the frame interface with the two walls and the drive unit, since the axially movable holding of the through-bolt on the first wall acts as a floating bearing, while the fastening on the second wall acts as a fixed bearing.
Further preferably, the drive assembly further comprises a tolerance compensating element. The first wall here also has a first wall opening. The tolerance compensating element is configured in the form of a sleeve and is arranged in the first wall opening. The through-bolt has a bolt head, which is arranged in the tolerance compensation element. In particular, tolerance compensation elements are provided in order to achieve a play-free arrangement between the screw head and the first wall in the radial direction of the wall opening. Alternatively, the bolt shank of the through-bolt can be arranged in the tolerance compensation element, wherein in this case the through-bolt is preferably movable together with the tolerance compensation element in the axial direction relative to the first wall. By providing the tolerance compensation element as an additional component, tolerance compensation can be achieved in a particularly simple manner and with precise adaptation to the individual tolerance conditions.
Particularly preferably, the tolerance compensation element has a plain bearing bush and a damping cap, wherein the damping cap surrounds the plain bearing bush. For example, the damping cap can completely surround the plain bearing bush in the circumferential direction. Alternatively, the damping cap can have one or more hollows. Preferably, the plain bearing bush is thus arranged radially inside. In this way, a low-friction sliding contact is provided between the screw head and the tolerance compensation element, as a result of which unintentional axial clamping between the through-screw and the first wall can be avoided in a particularly reliable manner. The damping cap can thereby prevent or reduce the transmission of vibrations between the first wall and the screw head, and ensure a reliable fastening of the tolerance compensation element in the wall opening. Preferably, the damping cover is formed of an elastomer.
The plain bearing bush and the screw head are preferably designed such that when the screw head is arranged in the tolerance compensation element, in particular in the fully clamped state, the screw head widens the plain bearing bush in the radial direction. This can be achieved, for example, by means of a corresponding fit between the bolt head and the plain bearing bush. The sliding bearing bush is preferably designed to taper on its inner circumference in the direction toward the drive unit, the screw head having a larger diameter. In this way, the tolerance compensation element is pressed radially by the screw head into the wall opening of the first wall, as a result of which a particularly secure and secure holding is achieved. Furthermore, radial tolerances can thereby be reduced to zero.
Preferably, the plain bearing bush is configured to be slotted. This makes it possible to cause radial widening particularly simply and specifically. Furthermore, it is thereby possible to facilitate the pressing of the tolerance compensating element into the wall opening.
Preferably, the slit of the plain bearing bush is arranged obliquely with respect to the axial direction of the plain bearing bush, in particular when the slit is viewed from the radial direction. Thereby, an optimized uniform mechanical support can be provided around the entire circumference and over the entire axial length of the plain bearing bushing.
It is particularly preferred that the damping cap has at least one sealing lip on the radially outer side. At least one sealing lip is preferably arranged on the axial end of the damping cap. Preferably, sealing lips are arranged on both axial ends. The at least one sealing lip is configured in such a way that, when the tolerance compensating element is arranged in the first wall opening, an axial form fit is present between the damping cap and the first wall. In other words, the tolerance compensating element can be clamped into the first wall opening by means of the sealing lip. In this way, a particularly simple and reliable holding of the tolerance compensation element can be achieved. Furthermore, a particularly reliable sealing effect is provided on the first wall opening.
Particularly preferably, the damping cap is configured such that, when the screw head of the through-screw is located in the tolerance compensation element, the at least one sealing lip is pressed radially outwards by the screw head. Preferably, the further sealing lip projects here on the radially inner side of the tolerance compensation element, which is pressed radially outward by the screw head, in order to thus also press the radially outer sealing lip outwards. Preferably, the two sealing lips are arranged on the side of the tolerance compensation element facing the drive unit. This ensures that the sealing lip is always placed in the direction of the drive unit and radially outward. For example, it is thereby also prevented that a part of the sealing lip moves inwards in the direction towards the plain bearing bush due to friction.
Preferably, the sliding bearing bush has a radially outwardly projecting latching lug on at least one axial end, preferably on both axial ends. In particular, the latching lugs project radially outwards from the cylindrical base body of the slide bearing bush. By means of the latching lugs, a secure fastening of the tolerance compensation element in the wall opening of the first wall can be achieved, in particular by means of a form fit between the latching lugs of the slide bearing bush and the first wall. Preferably, the plain bearing bush can be compressed during installation through the gap in order to achieve a simple installation. The latching lugs can preferably extend around the entire circumference of the plain bearing bush or alternatively preferably extend over only a part of this circumference.
Preferably, the through-bolts are fastened to the second wall, in particular by means of a screw connection. The through-bolts clamp the two sleeves and the second wall relative to one another. Furthermore, the through-bolts are held on the first wall by means of the holding element. The retaining element secures the through-bolt to the first wall in the radial direction. In particular, the retaining element centers the through-bolt relative to the wall opening of the first wall. In other words, an additional component is provided by means of the retaining element, which additional component provides radial tolerance compensation for the through-bolt on the first wall. In this way, a particularly precise fastening with minimal tolerances can be achieved.
Preferably, the holding element has an external thread, by means of which the holding element is screwed into an internal thread of the wall opening of the first wall. The holding element also has a holding opening in which the bolt head of the through-bolt is held. The holding opening is configured in this case such that it widens in the direction toward the second wall. Alternatively or additionally, the bolt head of the through bolt is configured to taper in a direction towards the first wall. Preferably, the widened portion of the wall opening and/or the taper of the screw head is configured conically. In the case of wall openings and bolt heads which are both designed to be widened or thinned, these wall openings preferably have the same taper angle. The widening or tapering makes it possible in a particularly simple manner and precisely to radially fix the through-bolt to the first wall, in particular in such a way that precise centering with respect to the opening of the first wall is additionally achieved.
Preferably, the screw head of the through screw is arranged in the wall opening of the first wall. The screw head has a particularly preferably external thread, to which the holding element is screwed, in particular by means of an internal thread of the holding element. The holding element has a side surface that tapers in the direction of the second wall. Alternatively or additionally, the wall opening of the first wall is configured to taper in a direction towards the second wall. Preferably, the side surfaces and/or the tapering of the wall opening are configured as conical tapering. In the case of the side surfaces of the holding element and the wall opening both being configured to taper, the respective conical tapers preferably have the same cone angle. Thanks to these tapering, the radial fastening of the through-bolt to the first wall can be achieved in a particularly simple and precise manner by screwing the retaining element onto the bolt head, in particular in such a way that additionally a precise centering of the bolt and the retaining element with respect to the wall opening is achieved.
Preferably, the holding element is formed from plastic and/or has a rubber element and/or a plastic element on the contact surface of the holding element with the screw head. This prevents noise, such as squeak, from being generated by the drive assembly during its operation.
Further preferably, each sleeve has a pinched region. In this case, a press fit is formed between the compression region and the through-bore. A particularly reliable and defined retention and force transmission between the sleeve and the drive unit can thus be achieved.
Preferably, the compression region is arranged adjacent, in particular immediately adjacent, to the flange. The shaft of each sleeve additionally has a tapering region, which has a smaller outer diameter than the compression region. In particular, the tapering region is thus arranged on the side of the compression region opposite the flange. Hereby is achieved that the tapering region can be introduced simply and smoothly into the through-bore of the drive unit, so that the sleeve can be inserted simply into the through-bore.
Preferably, the through-bore has a centering region which is arranged centrally in the through-bore and which has a smaller inner diameter than the remainder of the through-bore. The centering region is provided for centering the two sleeves in the through-bore, in particular by means of the respective tapering region. Preferably, a clearance fit is formed between each tapering region and the centering region, so that the sleeve can be inserted smoothly, but the centering region is oriented precisely centrally in the through-bore for optimal orientation of the two sleeves.
Particularly preferably, the through-bolts are configured as screws and are screwed into the internal thread of the second wall. In this way, a particularly simple, cost-effective and lightweight drive assembly can be provided, which is produced with few components.
Preferably, the through-bolts are configured as screws and are screwed into nuts arranged on the second wall. This can provide a particularly robust screw-on, since, for example, the through-bolts and nuts can be made of a harder material than the frame interface. For example, by using through bolts and nuts made of steel, particularly high torque can be used for screwing. Furthermore, the nut can be replaced simply in case of damage to the internal thread. The use of a nut has another advantage: the nut, due to the radially predefined play, exhibits tolerance compensation with respect to the wall opening of the first wall and is thus always aligned precisely.
Preferably, the nut is arranged in the notch of the second wall in a rotationally fixed manner. For example, the nut and the slot can have a non-circular geometry here, for example in the form of a tangential flattened portion, in particular with respect to the axis of the through opening through the second wall. Hereby a particularly simple installation of the drive assembly is achieved.
It is further preferred that the flange of the at least one sleeve has a predetermined thickness, in particular in a direction parallel to the longitudinal direction of the sleeve, which is substantially equal to the wall thickness of the rod, in particular in the radial direction. Alternatively, the flange of at least one sleeve preferably has a predetermined thickness, in particular in a direction parallel to the longitudinal direction of the sleeve, which is at least 1.5 times, preferably at least twice, particularly preferably at least three times, in particular in the radial direction, the wall thickness of the rod. Thus, a variable width of the drive assembly can be provided, which enables adaptation of frame interfaces of different widths in a particularly simple and cost-effective manner.
Preferably, the drive unit has a motor and/or a transmission. By means of the specific arrangement and retention between the walls of the frame interface, an optimally reliable connection with an advantageous mechanical force distribution can be provided in order to achieve a long service life of the drive unit. Furthermore, a low weight of the drive assembly can be achieved in a simple and cost-effective manner.
Furthermore, a vehicle, preferably a vehicle which can be driven with muscle force and/or motor force, preferably an electric bicycle, is disclosed, which vehicle comprises the described drive assembly. The frame interface can be, for example, a part of a vehicle frame of a vehicle.
Preferably, the vehicle comprises a vehicle frame. The frame interface of the drive assembly is a component of the vehicle frame, i.e. the vehicle frame is formed as a one-piece component with the frame interface, wherein the drive unit is preferably connected directly, i.e. in particular without additional components between them, to the frame interface. Alternatively, preferably, the frame interface of the drive assembly and/or one or both of the walls of the frame interface are configured as separate components relative to the vehicle frame and are connected, preferably screwed, to the vehicle frame. Thus, for example, the drive unit can be fastened indirectly to the frame interface.
Particularly preferably, the vehicle further comprises a chain wheel, which is connected to the output shaft of the drive unit. The second wall of the drive assembly is arranged here on the side of the chain wheel. In particular, when the fastening is formed as a fixed bearing on the second wall and as a floating bearing on the first wall, an optimized direct force transmission between the drive unit and the chain wheel is thereby enabled. In addition, precise positioning of the chain plate, i.e. precise positioning of the precise chain line, is ensured.
Drawings
Hereinafter, the present invention is described with reference to the embodiments in conjunction with the accompanying drawings. In the drawings, functionally identical components are respectively identified by the same reference numerals. Here, it is shown that:
figure 1 is a simplified schematic illustration of a vehicle having a drive assembly according to a first embodiment of the invention,
figure 2A is a cross-sectional view of the drive assembly of figure 1 in a fully tightened state,
figure 2B is a cross-sectional view of the drive assembly of figure 1 prior to tightening,
figure 3 is a detail of figure 2A,
figure 4 is a perspective detail view of the installation of the drive assembly of figure 2A,
figure 5 is a perspective detail view of a tolerance compensating element of a drive assembly according to a second embodiment of the present invention,
figure 6 is a cross-sectional view of a drive assembly according to a third embodiment of the invention,
Figure 7 is a cross-sectional view of a drive assembly according to a fourth embodiment of the invention,
figure 8 is a cross-sectional view of a drive assembly according to a fifth embodiment of the invention,
figure 9 shows a detail of a drive assembly according to a sixth embodiment of the invention,
figure 10 is a detailed cross-sectional view of figure 9,
figure 11 is a detailed cross-sectional view of a drive assembly according to a seventh embodiment of the invention,
figure 12 is another detailed cross-sectional view of the drive assembly of figure 11,
figure 13 is a cross-sectional view of a drive assembly according to an eighth embodiment of the invention,
figure 14 is a cross-sectional view of a drive assembly according to a ninth embodiment of the invention,
figure 15 is a cross-sectional view of a drive assembly according to a tenth embodiment of the invention,
figure 16 is a cross-sectional view of a drive assembly according to an eleventh embodiment of the invention,
figure 17 is a detailed cross-sectional view of a drive assembly according to a twelfth embodiment of the invention,
FIG. 18 is another detailed cross-sectional view of a drive assembly according to a twelfth embodiment of the invention, an
Fig. 19 is a detailed cross-sectional view of a drive assembly according to a thirteenth embodiment of the invention.
Detailed Description
Fig. 1 shows a simplified schematic of a vehicle 100 drivable in muscle and/or motor force, which vehicle comprises a drive assembly 1 according to a first embodiment of the invention. The vehicle 100 is an electric bicycle. The drive assembly 1 is arranged in the region of a pedal bearing and comprises a drive unit 2. The drive unit 2 comprises an electric motor and a transmission and is provided for supporting a pedal force of the driver by means of muscle force by means of a torque generated by the electric motor. The drive unit 2 is supplied with electrical energy from an electrical energy store 109.
The drive assembly 1 of the first embodiment is shown in a cross-sectional view in fig. 2A. The drive assembly 1 comprises a U-shaped frame interface 3 in which the drive unit 2 is partly received. The frame interface 3 is an integral part of the vehicle frame 105 of the vehicle 100 (see fig. 1). The frame interface 3 has a first wall 31 and a second wall 32, between which the drive unit 2 is arranged. The first wall 31 and the second wall 32 are connected to each other by a connecting wall 33 and thus constitute a common integral member.
The drive unit 2 is fastened to the frame interface 3 by means of a threaded screw, as described further below.
In detail, the drive unit 2 has a through-bore 20a which extends completely through the drive unit 2 in the transverse direction. In particular, the through-bore 20 is formed in a housing of the drive unit 2, which is preferably formed from aluminum or magnesium. The housing of the drive unit 2 can be constructed in two parts, wherein a housing seal 2c is arranged between the two housing halves 2a, 2 b.
Two sleeves 41, 42 are inserted into the through-bore 20. The two sleeves 41, 42 are each inserted into the through-bore 20 here starting from one side, i.e. at the axial end of the through-bore 20. The sleeves 41, 42 are preferably formed of aluminum or steel.
Each sleeve 41, 42 has a rod 43, which is configured essentially as a hollow cylinder and is inserted into the through-bore 20, and a flange 44. The flange 44 is arranged outside the through-bore 20 and has a larger outer diameter than the rod 43.
The lever 43 has a contact region 43a, which is arranged next to the flange 44. The compression region 43a is configured in such a way that a press fit, i.e. an interference fit, is formed between the compression region 43a and the through-bore 20.
A taper region 20a is formed in the middle of the through-hole 20, in which the inner diameter of the through-hole 20 tapers. A preferably clearance fit is constructed between the tapered region 20a and the sleeves 41, 42. The tapering region 20a thus brings about a centering of the sleeves 41, 42 and thus a particularly precise arrangement of the sleeves 41, 42.
Preferably, the two sleeves 41, 42 are identical in construction for simple and cost-effective production.
The axial length of the sleeves 41, 42, in particular of the respective rods 43, is designed such that the sleeves 41, 42, in the inserted and fully screwed state (as will be described later), come into contact with one another in the through-bore 20.
Furthermore, the drive assembly 1 comprises a through-bolt 5 which is inserted through the through-bore 20 and the two sleeves 41, 42. The through-bolt 5 is designed as a screw and has a screw head 53 at one axial end and an external thread 54 at the other axial end, wherein the external thread 54 extends only over a partial region of the through-bolt 5.
The through-bolt 5 is screwed into the nut 51 on the second wall 32 by means of the external thread 54. The screw head 53 is located on the side of the first wall 31 and in particular rests on the outside of the first wall 31.
Preferably, a clearance fit is constructed between the through-bolts 5 and the inner through-openings of the sleeves 41, 42, respectively, in order to achieve a simple penetration. On the area of the through-bolt 5 within each sleeve 41, 42, a seal, for example an O-ring seal 56, is preferably arranged between the through-bolt 5 and the sleeve 41 or 42, respectively, in order to avoid the ingress of fluid into the interior of the sleeve 41, 42 and into the interior of the through-bore 20.
The through-bolt 5 is screwed in such a way that it clamps the two sleeves 41, 42 against the second wall 32 in the axial direction of the through-bolt 5. By means of the sleeves 41, 42, it is ensured here that such clamping does not lead to a pressure load of the drive unit 2 in the axial direction between the flanges 44 of the two sleeves 41, 42 or to a precisely defined pressure load. In particular, the tensile load of the drive unit 2 is avoided by the two sleeves 41, 42.
The particular threaded screw-on of the drive assembly 1 offers a number of advantages here. For example, the use of the through-bolts 5 allows a particularly robust fastening of the drive unit 2. In particular, screwing can be performed with high torque. By receiving high pressures by means of the sleeves 41, 42, unacceptably high mechanical stresses on the drive unit 2 are avoided in this case in a particularly reliable manner. Furthermore, the tolerance position of the drive assembly 1 can be set in a defined manner in a simple and cost-effective manner, for example by adapting the sleeves 41, 42. Furthermore, the threaded screw-on allows a particularly simple installation of the drive assembly 1, since the insertion of the through-bolts 5 and the manipulation of the through-bolts 5 for screwing in can be performed from only one side, i.e. the side of the first wall 31. This is particularly advantageous in situations where accessibility to the side of the second wall 32 is limited, such as when the chain tray 106 is located on that side (see fig. 1).
Additionally, each sleeve 41, 42 comprises a damping element 45 formed of a resilient and vibration damping material. In particular, the damping element 45 is formed of an elastomer. In detail, the radially outer side of the flange 44 and the side of the flange 44 facing the drive unit 2 of the lever 43 are covered or coated with a damping element 45. Preferably, the damping element 45 is thus configured in the form of an envelope of the sleeve 41, 42.
Furthermore, the axial length of the rods 43 of the sleeves 41, 42 is configured such that, in the state of complete insertion into the through-bore 20 but not yet clamped by the through-bolt 5, as shown in fig. 2B, a predefined axial distance 27, i.e. a gap, exists between the two sleeves 41, 42 in the interior of the through-bore 20. Consider here the state: in this state, the two sleeves 41, 42 are not clamped, but the damping element 45 rests against the drive unit 2 in the region of each flange 44 of each sleeve 41, 42. In particular, the axial length of the two rods 43 is smaller than half the axial length of the through-bore 20 by a predetermined difference, wherein the predetermined difference is smaller than twice the thickness of one of the damping elements 45 in the region of the flange 44.
In the fully screwed state shown in fig. 2A, a predefined gap 29 is present between the first wall 31 and the first sleeve 41.
By this specific coordination of the lengths of the two sleeves 41, 42 and the length of the through-bore 20, the portion of the damping element 45 of each sleeve 41, 42 between the flange 44 and the drive unit 2 is respectively compressed or clamped between the flange 44 and the drive unit 2 by the clamping effected by means of the through-bolts 5 and is thereby elastically deformed.
The corresponding design of the damping element 45 and the sleeves 41, 42 with an axial distance in the undamped state results in a slight pressure load being applied to the drive unit 2 in the clamped state. This can advantageously affect the tightness of the drive unit 2 itself. Furthermore, a particularly reliable seal between the sleeves 41, 42 and the drive unit 2 can be achieved by elastic deformation of the damping element 45.
Fig. 1 also shows an output shaft 108 of the drive unit 2, which is connected in a rotationally fixed manner to the chain wheel 106. The output shaft 108 can be driven by the muscle force of the driver on the one hand and by the motor force of the drive unit 2 on the other hand. Here, the chain tray 106 is located on the side of the second wall 32. As already mentioned above, an advantageous accessibility and a simplified installation of the drive assembly 1 are thereby obtained. Furthermore, the advantage is thereby obtained that a direct force transmission between the output shaft 108 and the frame interface 3, which can be received particularly well by the direct and robust attachment achieved by means of the second wall 32, due to the high mechanical forces on the chain-disk side. Furthermore, a defined position of the chain disk 106 with respect to the axial direction of the output shaft 108 and with respect to the frame interface 3 is thereby ensured, which brings about the advantage of a reliably and precisely arranged chain line.
Furthermore, by connecting the drive unit 2 to the frame interface 3 via the damping element 45, the advantage is obtained that the drive unit 2 is held on the vehicle 100 in a vibration-decoupled manner. In addition to preventing or reducing acoustic vibration transmission, this has the beneficial effect of reducing noise while the vehicle 100 is in operation, as well as reducing or preventing transmission of mechanical vibrations. Thereby preventing or reducing the damaging effects of such vibrations on the screw. That is, loosening or reprocessing of the screw portion can be prevented or reduced. Furthermore, due to the elasticity of the damping element 45 itself, a certain tolerance compensation can be made, for example in terms of the coaxiality of the bore or opening etc.
Additionally, an axially movable holding of the through-bolt 5 is provided on the first wall 31. Here, the bolt head 53 of the through bolt 5 is located in the wall opening 31a of the first wall 31. The deformation of the first wall 31 is thus not provided, but a particularly rigid and robust frame interface 3 can be provided.
The axially movable holding is achieved by means of a tolerance compensation element 7. This holding by means of the tolerance compensation element 7 is shown enlarged in fig. 3. The tolerance compensating element 7 here comprises a hollow cylindrical plain bearing bush 71 and a damping cap 72. The damping cover 72 is constructed in particular from an elastic material, preferably an elastomer. The damping cap 72 substantially completely surrounds the radially outer side of the plain bearing bush 71, wherein, for example, notches (not shown) can also be provided in the damping cap 72. Additionally, the damping cap at least partially covers both axial end sides of the plain bearing bush 71. On the radially inner side, the slide bearing bush 71 is exposed, so that the bolt head 53 can be moved smoothly with a small friction force relative to the tolerance compensation element 7.
Preferably, the plain bearing bush 71 can be formed from a solid material in the circumferential direction or alternatively be configured as slotted, i.e. with a longitudinal slot in the axial direction. In both cases, the plain bearing bush 71 is preferably designed in such a way that, by screwing in the through-bolt 5 and thus by penetrating the bolt head 53 into the plain bearing bush 71, the plain bearing bush 71 is widened in the radial direction in such a way that a press fit is formed between the tolerance compensation element 7 and the wall opening 31 a. Thereby, it is possible to hold the bolt head 53 in the wall opening 31a without play in the radial direction.
Here, the gap 29 between the first wall 31 and the first sleeve 41 exists both in the unthreaded state and in the fully threaded state (see fig. 2A and 3).
Preferably, the bolt head 53 has an insertion chamfer 53a (see fig. 3) on the side facing the sleeve 41, which facilitates the pushing in and screwing in of the through-bolt 5.
The damper cap 72 has seal lips 72a, which are configured as lips protruding not only radially inward but also radially outward, on both axial ends, respectively. Here, due to the elasticity of the damper cap 72, the seal lip 72a is pressed radially outward by the bolt head 53 when the through bolt 5 is screwed in. Thereby, a reliable and defined seal is formed between the first wall 31 and the tolerance compensating element 7 and between the bolt head 53 and the tolerance compensating element 7. Furthermore, the sealing lip 72a causes an axial form-locking of the tolerance compensating element 7 with the first wall 31. A reliable and defined arrangement of the tolerance compensating element 7 relative to the first wall 31 is thereby ensured.
As shown in fig. 4, the tolerance compensation element 7 can preferably be inserted into the wall opening 31a of the first wall 31 from the outside, i.e. from outside the frame interface 3, before the drive unit 2 is arranged, in particular by means of a slight form fit of the sealing lip 72 a.
Additionally, the screwing of the through-bolt 5 in the first embodiment is configured on the second wall 32 by means of a nut 51. The through-bolt 5 is screwed into a nut 51 on the second wall 32. The nut 51 may preferably also be formed from steel, as is the case with the through-bolt 5, in order to be able to achieve a particularly firm screwing with high torque.
The nut 51 is arranged in a rotationally fixed manner in the recess 32b of the second wall 32. The slot 32b is preferably an external radial extension of the circular second wall opening 32c that extends through the second wall 32. As can be seen in fig. 4, the slot 32b has two opposing flattened portions 32d, i.e. two straight and parallel walls arranged in tangential direction. The nut 51 has a corresponding geometry with two opposed flats 51 a. The flattened portions 32d, 51a result in this case in that the nut 51 cannot be twisted in the second wall 32, for example when screwing in the through-bolt 5, as a result of which a particularly simple and rapid installation of the drive assembly 1 is achieved.
Furthermore, the nut 51 is configured in a T-shape in a sectional view. In this way, a maximum thread length can be provided with an optimal compactness of the entire drive assembly 1, so that a firm and reliable screwing with the through-bolt 5 can be achieved.
Fig. 5 shows a perspective detail view of a tolerance compensating element 7 of a drive assembly 1 according to a second embodiment of the invention. The second embodiment essentially corresponds to the first embodiment of fig. 1 to 4, with the difference that the slide bearing bush 71 of the tolerance compensation element 7 has an alternative configuration. The plain bearing bush 71 is shown in fig. 5 in a perspective view.
The plain bearing bush 71 has a longitudinal slot 77 which extends completely through the substantially hollow-cylindrical plain bearing bush 71 in the axial direction and in the radial direction. Here, the longitudinal slot 77 is arranged obliquely with respect to the longitudinal axis 70 of the plain bearing bush 71, i.e. it extends along such a line: the line is arranged at an angle of preferably at least 5 °, preferably at most 45 °, to the longitudinal axis 70 when projected radially onto the plane of the longitudinal axis 70. An optimal mechanical support around the entire circumference of the plain bearing bush 71 can thereby be provided, since there is no interruption or only a slight interruption of the projected bearing surface, for example, between the screw head 53 and the first wall 31. This enables, for example, a better coaxial positioning accuracy of the drive unit 2 relative to the frame interface 3.
The slide bearing bush 71 of fig. 5 also has a latching lug 78 on the outer periphery on each axial end. The latching lugs 78 are formed as elements protruding from the outer periphery of the slide bearing bush 71 and cause a stronger form-locking with the first wall 31 (see also fig. 3 for this purpose). As can be seen in fig. 5, the two latching lugs 78 shown are each located next to the longitudinal slot 77, wherein the two latching lugs 78 are arranged on opposite sides of the longitudinal slot 77 with respect to the circumferential direction. Each of the two latching lugs 78 extends only over a portion of the circumference of the slide bearing sleeve 71. Preferably, further (not shown) latching lugs 78 can also be provided distributed around the circumference of the plain bearing bush 71.
The slide bearing bush 71 of fig. 5 also has a plurality of notches 79 on each axial end in a circumferentially distributed manner, which notches are configured essentially U-shaped and extend completely through the slide bearing bush 71 in the radial direction. By means of the notches 79 more material of the damping element 72 is available, which material connects the layer of the damping element 72 on the outer circumference of the plain bearing bush 71 with the radially inner layer. Thereby an optimal coupling of the plain bearing bushing 71 with the damping element 72 can be established.
The coupling of the slide bearing bush 71 with the damping element 72 is further optimized by a shoulder 71b on the inner periphery of the slide bearing bush 71. The shoulder 71b is provided here as an enlargement of the inner diameter of the plain bearing bush 71, which enlargement starts from the sliding surface 71 a. That is, the radially inner region of the damping element 72 can be arranged in shoulders 71b, each of which is located on an axial end of the plain bearing bush 71, respectively.
Fig. 6 shows a cross-sectional view of a drive assembly 1 according to a third embodiment of the invention. The third embodiment essentially corresponds to the first embodiment of fig. 1 to 4, with the difference that the damping elements 45 are arranged only on the flange 44 of the corresponding sleeve 41, 42. I.e. the damping elements 45 are each configured as disk-shaped and are arranged only between the side of the flange 44 facing the drive unit 2 and the drive unit 2.
Fig. 7 shows a cross-sectional view of a drive assembly 1 according to a fourth embodiment of the invention. Fig. 7 shows a detail of the drive assembly 1 according to a fourth embodiment of the invention. The fourth embodiment essentially corresponds to the first embodiment of fig. 1 to 4, with the difference that instead of the tolerance compensation element, a holding element 55 is provided on the first wall 31. Unlike the tolerance compensation elements of fig. 1 to 4, the holding element 55 brings about an axially movable holding of the screw head 53. Furthermore, the retaining element 55 causes the bolt head 53 to be fastened to the first wall 31 completely free of play in the radial direction.
The holding element 55 is in this case configured as a nut which can be screwed into the internal thread 31f of the wall opening 31a of the first wall 31. The holding element 55 has a holding opening 55c in which the bolt head 53 of the through bolt 5 is held. The holding opening 55c is configured to widen conically in the direction toward the second wall 32.
Additionally, the bolt head 53 has a tapered side surface 53b corresponding to the tapered geometry of the retaining opening 55 c. That is, the bolt head 53, in detail, the side surface 53b thereof is configured to taper in a direction toward the first wall 31. The corresponding taper angles of the side surfaces 53b and the holding opening 55c are the same.
In the installation of the drive assembly 1 of fig. 7, in this case, similar to the drive assembly 1 of fig. 1 to 4, a clamping with the second wall 32 is first established, i.e. the drive unit 2 is screwed to the second wall 32 by means of the through-bolts 5. The holding element 55 can then be screwed down until the screw head 53 is additionally clamped in the direction of the second wall 32. By holding the tapered surfaces of the opening 55c and the side surface 53b, the bolt head 53 is centered in the wall opening 31a in the radial direction so that the radial play is reduced to zero. In particular, an exact orientation of the bolt axis 50 coaxially with the opening axis 37 is thus achieved, on which the two wall openings 31a, 32c lie.
Fastening by means of the holding element 55 offers the following additional advantages: high tolerances on the first wall 31 can be compensated for in a simple manner and effectively.
Fig. 8 shows a cross-sectional view of a drive assembly 1 according to a fifth embodiment of the invention. The fifth embodiment essentially corresponds to the fourth embodiment of fig. 7, with the difference that the retaining element 55 and the bolt head 53 are in an alternative configuration. In the fifth embodiment of fig. 8, a screw thread is provided between the screw head 53 and the holding element 55 by means of an internal thread and an external thread 53 c. In detail, the holding element 55 is screwed onto the external thread 53 of the bolt head 53.
Further, in the fifth embodiment of fig. 8, the outer side surface 55b of the holding member 55 is configured to taper conically in a direction toward the second wall 32. Further, the inner side surface of the wall opening 31a is configured to taper conically in a direction toward the second wall 32. The taper angles of the two side surfaces are identical here. Thus, substantially the same effect as in the fourth embodiment of fig. 7 is obtained: the screw head 53 is radially centered relative to the wall opening 31a, with the difference that the retaining element 55 screwed to the screw head 53 is also additionally centered. In the fifth embodiment, in contrast to the fourth embodiment of fig. 7, the forces are also introduced in opposite directions onto the through-bolts 5 by the centering achieved by means of the holding elements 5.
Fig. 9 shows a detail of the drive assembly 1 according to a sixth embodiment of the invention. The sixth embodiment essentially corresponds to the first embodiment of fig. 1 to 4, with the difference that the sleeves 41, 42 are replaced.
Only one of the two sleeves 41, 42 is shown in fig. 9, wherein the two sleeves 41, 42 are preferably identical in design. The sleeve 41 is shown in a perspective view in fig. 10.
The sleeve 41 includes a stem 43 and a flange 44. The rod 43 is inserted into the through-bore 20 of the drive unit 2. The flange 44 is provided for abutment against the inner side of the second wall 32 of the frame interface 3 (see e.g. fig. 2A). The flange 44 of the sleeve 41 has a plurality of protruding form-locking elements 41c on the side assigned to the wall 32. Preferably, the form-locking elements 41c are arranged in one or more, preferably two circles as shown in fig. 9, which circles are arranged concentrically with the through-opening of the sleeve 41.
The individual form-locking elements 41c of the sleeve 41 of fig. 9 are shown in fig. 10 in a detail section. Each of the form-locking elements 41c has a pyramid 41d protruding from the surface 41f of the flange 44. Alternatively, each form-locking element 41c may also have a protruding cone. The pyramid 41d is configured as a straight pyramid and has a cone angle 41k of preferably less than 60 °. The pyramids 41d are caused to be pressed into the surfaces of the wall 32 when the sleeve 41 is screwed to the wall 32, i.e. the surfaces are plastically deformed. As a result, a slight form-locking between the sleeve 41 and the wall 32 is produced in a plane perpendicular to the screw axis, as a result of which a particularly secure connection of the drive unit 2 and the frame interface 3 to one another is possible. This can reliably prevent the drive unit 2 from slipping relative to the frame interface 3.
In this case, each form-locking element 41c has, in addition to the pyramid 41d, a recess 41e which is formed on the outer circumference of the pyramid 41d and in the surface 41f of the flange 44. The recess 41e can receive, for example, wall 32 material pressed into the wall 32 as a result of the intrusion of the pyramid 41d, so that the wall 32 and the flange 44 can lie reliably and precisely on one another. For example, a separate recess 51e can be provided for each pyramid 41d, which recess partially or completely surrounds the pyramid 41d. Alternatively, a single recess 41e can be configured in the surface 41f of the flange 44, on the radial inner side and/or outer side of which the pyramid 41d is arranged.
Fig. 11 shows a detailed cross-sectional view of a drive assembly 1 according to a seventh embodiment of the invention. In fig. 11, only one of the sleeves 41, 42, i.e. the sleeve 42 on the side of the second wall 32, is shown here. Preferably, the first sleeves 41 on the first wall 31 are identical in construction. The seventh embodiment essentially corresponds to the first embodiment of fig. 1 to 4, with the difference that an alternative configuration of the sleeve 42 in the region of the flange 44 is provided. Here, the sleeve 42 has a taper 41g on the radially outer end of the flange 44 on the side of the flange 44 facing the rod 43. The taper 41g is designed in such a way that the difference between the maximum thickness 41h and the minimum thickness 41i of the flange 44 corresponds to at least 50%, preferably at most 150%, of the wall thickness 43h of the shaft 43 of the sleeve 42. Here, the thickness is viewed in a direction parallel to the longitudinal axis of the sleeve 42.
The damping element 45 is designed in such a way that it compensates for the taper 41g of the flange 44. Additionally, the damping element 45 has a thickening 42g at the radially outermost end. Thus, there is a particularly thick damping element 42 on the radially outer end of the flange 44. This advantageously affects the optimal seal between the sleeve 42 and the drive unit 2.
Further, this seal is supported by a protruding annular rib 2g of the drive unit 2, which is provided in the seventh embodiment, as shown in fig. 12. The protruding annular rib 2g has a trapezoidal cross section and is arranged concentrically with the through-bore 20 of the drive unit 2. In the state in which the sleeve 42 is pressed into the through-bore hole 20, the protruding annular rib 2g and the taper 41g of the sleeve 42 are located here at the same radius with respect to the bore axis 20g of the through-bore hole 20. The protruding annular rib 2g thus dips into the soft region of the damping element 45 in the region of the taper 41g, if the sleeve 42 and the drive unit 2 are pressed against one another in the fully screwed state. Thus, sealing is optimally performed at the drive unit 2 by the elastic properties of the damping element 45.
Fig. 13 shows a cross-sectional view of a drive assembly 1 according to an eighth embodiment of the invention. The eighth embodiment essentially corresponds to the first embodiment of fig. 1 to 4, with the difference that the drive unit 2 is screwed indirectly to the frame interface 3. In detail, the two walls 31, 32 are embodied as separate components relative to the frame interface 3, to which the drive unit 2 is screwed. For example, the walls 31, 32 can be configured as retaining plates. The walls 31, 32 can be connected to the frame walls 31e, 32e of the frame interface 3 by means of additional screw connections 30 and/or welded connections (not shown). This provides a particularly high flexibility of the drive assembly 1.
Fig. 14 shows a sectional view of a drive assembly 1 according to a ninth embodiment of the invention. The ninth embodiment essentially corresponds to the first embodiment of fig. 1 to 4, with the difference that the sleeves 41, 42 are of alternative configuration. In the ninth exemplary embodiment of fig. 14, the two sleeves 41, 42 are formed as shortened metal sleeves which can be produced particularly simply and cost-effectively. The sleeves 41, 42 are designed such that they do not touch one another in the through-bore 20. Furthermore, the two sleeves 41, 42 have a short axial length 41l, which is, for example, smaller than the inner diameter of the through-bore 20. This saves material and also enables simple pressing of the sleeves 41, 42 into the through-bore 20, since only short pressing lengths are present. Thus, the drive assembly 1 of the ninth embodiment achieves a particularly simple and cost-effective construction.
Fig. 15 shows a cross-sectional view of a drive assembly 1 according to a tenth embodiment of the invention. The tenth embodiment essentially corresponds to the seventh embodiment of fig. 11 and 12, with the difference that alternative sleeves 41, 42 are used. In detail, the flanges 44 of the sleeves 41, 42 in the tenth embodiment of fig. 15 are implemented to be thicker than in the seventh embodiment. In detail, the thickness 41h of the flange 44 in the tenth embodiment is a multiple, preferably at least three times, the wall thickness 43h of the respective stem 43 of the corresponding sleeve 41, 42. The overall width 1h of the drive assembly 1 can thus be configured to be greater than in the seventh embodiment, in which the thickness 41h of the flange 44 is, for example, approximately equal to the wall thickness 43h of the rod 43. The tenth embodiment of fig. 15 thus shows that the drive assembly 1 can be adapted to different vehicles 100 particularly simply and cost-effectively by changing the sleeves 41, 42.
Fig. 16 shows a cross-sectional view of a drive assembly 1 according to an eleventh embodiment of the invention. The eleventh embodiment essentially corresponds to the first embodiment of fig. 1 to 4, with the difference that an alternative configuration of the floating support on the first wall 31 is provided. In the eleventh embodiment of fig. 16, the through-bolt 5 and the tolerance compensating element 7 are jointly supported in an axially movable manner relative to the first wall 31. In this case, unlike the first embodiment, not the screw head 53, but the shaft 53d of the through-screw 5 is arranged in the tolerance compensation element 7. In the eleventh exemplary embodiment, the through-bolt 5 additionally clamps the tolerance compensation element 7 against the first sleeve 41. Thus, the through bolt 5 and the tolerance compensating element 7 can slide jointly in the wall opening 31a of the first wall 31. The wall opening 31a also has an enlarged diameter 31b on the outside, so that the bolt head 53 can be arranged partly in the wall opening 31 a. Alternatively, the bolt head 53 can also be arranged completely outside the wall opening 31 a.
Fig. 17 shows a detailed cross-sectional view of a drive assembly 1 according to a twelfth embodiment of the invention. The twelfth embodiment essentially corresponds to the seventh embodiment of fig. 11 and 12, with the difference that the damping element 45 is in an alternative configuration. In the twelfth embodiment of fig. 17, the damping element 45 has a sealing projection 45a on the axial end of the sleeve 41 opposite the flange 44. The seal projection 45a protrudes beyond the end side 43c of the rod 43 of the sleeve 41 in the axial direction. Further, a seal projection 45a projects outwardly from the damping element 45 in the radial direction.
The axial extension 45f of the sealing projection 45a is preferably at least 20% of the wall thickness 43h of the rod 43. Furthermore, the radial projection 45g is preferably at least 30% of the wall thickness 43h of the stem 43.
The sealing projections 45a on the damping elements 45 of the sleeves 41, 42 here give rise to a particularly reliable seal against the ingress of fluid. This is achieved by pressing each sealing projection 45a axially and radially, as shown in fig. 18. By clamping the clamping sleeves 41, 42 against each other in the axial direction, the two sealing projections 45a are pressed against each other in the axial direction. For example, each sealing projection 45a can additionally be pressed in radial direction with the inner periphery 20g of the through-bore 20, additionally by a radial interference of the sealing projection 45a with respect to the inner periphery 20g of the through-bore 20. Thus, in the plane of the end sides 43c of the sleeves 41, 42 which are in contact with each other, a reliable seal is produced on the radially outer side of the rod 43 of the sleeves 41, 42 by means of the sealing projection 45 a.
Fig. 19 shows a detailed cross-sectional view of a drive assembly 1 according to a thirteenth embodiment of the invention. The thirteenth embodiment essentially corresponds to the twelfth embodiment of fig. 17 and 18, with the difference that the flange 44 of the sleeve 41, 42 is of alternative configuration. In the thirteenth embodiment of fig. 19, the flange 44 of the sleeve 42 is constructed in two pieces and comprises a flange base 44a and an insert ring 44b. The flange base 44a is configured together with the rod 43 of the sleeve 42 as a one-piece member. The insert ring 44a is configured concentric with the sleeve opening of the sleeve 42 and is arranged in a groove 44g of the flange base 44 a. The insert ring 44b is held in the groove 44g by an axial form fit 44 f. The axial form fit 44f can be produced, for example, by caulking, i.e., retrofitting, of a partial region of the flange base 44 a. In this case, the form-locking element 41c is in the thirteenth embodiment arranged only on the insert ring 44a and is formed as part of this insert ring.
The insert ring 44b is formed from hardened steel, which has a significantly higher hardness than the material of the flange base 44a and the rod 43. As a result, a particularly high robustness and thus a durable and reliable function of the form-locking element 41c can be ensured. Furthermore, by virtue of the two-piece design of the flange 44, both the flange base 44a and the rod 43 are formed from steel which is well suited for cold-forming. Thereby, the sleeves 41, 42 can be manufactured in a particularly simple and cost-effective manner.
Claims (37)
1. A drive assembly for a muscle and/or motor force drivable vehicle (100), the drive assembly comprising:
a drive unit (2),
-a frame interface (3),
-wherein the drive unit (2) is arranged at least partially between a first wall (31) and a second wall (32) of the frame interface (3), wherein the drive unit (2) has a through-bore (20),
-two sleeves (41, 42) inserted on both sides into the through-bore (20) of the drive unit (2), and
-a through bolt (5) which is inserted through the through-bore (20) and the two sleeves (41, 42) and which holds the drive unit (2) on each of the two walls (31, 32).
2. The drive assembly according to claim 1,
-wherein the two sleeves (41, 42) are in contact with each other within the through-bore (20) and
-wherein the through bolt (5) clamps the two sleeves (41, 42) against each other.
3. The drive assembly according to any one of the preceding claims,
wherein each sleeve (41, 42) has a stem (43) and a flange (44),
-wherein the rod (43) is at least partially arranged within the through-bore (20) and
-wherein the flange (44) is arranged outside the through-bore (20).
4. A drive assembly according to claim 3,
-wherein each sleeve (41, 42) has a damping element (45) arranged on the side of the flange (44) facing the drive unit (2) and
-wherein the damping element (45) is formed of a vibration absorbing material.
5. The drive assembly according to claim 4, wherein the damping element (45) additionally at least partially surrounds the rod (43).
6. The drive assembly according to claim 5, wherein the damping element (45) has, on an axial end opposite the flange (44), a sealing projection (45 a) protruding axially and radially from the rod (43).
7. The drive assembly according to claim 6, wherein the sealing projection (45 a) protrudes beyond an end side (43 c) of the rod (43) of the sleeve (41, 42) in an axial direction.
8. Drive assembly according to any of the preceding claims, wherein the two sleeves (41, 42) are designed such that in the fully pushed-in state into the through-bore (20) and in the undamped state there is a predefined axial distance (27) between the two sleeves (41, 42) within the through-bore (20).
9. Drive assembly according to claim 8, wherein the predefined axial distance (27) is designed such that in the clamped state the axial distance (27) is compensated by clamping of the two sleeves (41, 42) by means of the through-bolt (5) and by elastic deformation of the damping element (45).
10. The drive assembly according to any one of claims 3 to 9,
-wherein the flange (44) of at least one sleeve (41, 42) has a plurality of protruding form-locking elements (41 c) on the side facing the respective wall (31, 32), and
-wherein the form-locking element (41 c) is configured such that it is pressed into the wall (31, 32) by screwing with the corresponding wall (31, 32).
11. The drive assembly according to claim 10,
wherein the flange (44) is formed in two parts and comprises a flange base (44 a) and an insert ring (44 b),
-wherein the flange base (44 a) is configured as a one-piece component with the lever (43) and
-wherein the form-locking element (41 c) is arranged on the insert ring (44 b).
12. Drive assembly according to claim 11, wherein the insert ring (44 b) is arranged in a groove (44 c) of the flange base body (44 a), and in particular wherein the insert ring (44 b) is held in the groove (44 c) by means of an axial form fit.
13. The drive assembly according to any one of claims 11 or 12, wherein the flange base (44 a) and the insert ring (44 b) are formed of different materials, in particular wherein the insert ring (44 b) has a greater hardness than the flange base (44 a).
14. A drive assembly according to any one of claims 10 to 13, wherein each form-locking element (41 c) has a pyramid (41 d) protruding from a surface (41 f) of the flange (44) or has a cone.
15. The drive assembly according to claim 14, wherein each form-locking element (41 c) has a recess (41 e) in the surface (41 f) of the flange (44) adjoining the pyramid (41 d).
16. The drive assembly according to any one of claims 3 to 15,
-wherein the flange (44) of at least one sleeve (41, 42) has a taper (41 g) on the radially outer end and on the side facing the rod (43), and
-wherein the taper (41 g) is compensated by the damping element (45).
17. The drive assembly according to claim 16,
wherein the drive unit (2) has at least one protruding annular rib (2 g) which is arranged concentrically with one of the openings (20 a, 20 b),
-in particular wherein the protruding annular rib (2 g) and the taper (41 g) of the flange (44) of the sleeve (41) are arranged on the same radius with respect to a drilling axis (20 g) of the through-drilling (20).
18. The drive assembly according to any one of the preceding claims,
-wherein the through bolt (5) is fastened on the second wall (32) and
-wherein the through bolt (5) is axially movably held on the first wall (31).
19. The drive assembly according to claim 18, further comprising a tolerance compensating element (7),
-wherein the first wall (31) has a first wall opening (31 a),
-wherein the tolerance compensation element (7) is sleeve-shaped and arranged in the first wall opening (31 a) and
-wherein a bolt head (53) or a bolt shank (53 d) of the through bolt (5) is arranged within the tolerance compensation element (7).
20. Drive assembly according to claim 19, wherein the tolerance compensating element (7) has a plain bearing bushing (71) and a damping cap (72) surrounding the plain bearing bushing (71).
21. Drive assembly according to claim 20, wherein the plain bearing bushing (71) and the bolt head (53) are designed such that the bolt head (53) widens the plain bearing bushing (71) in the radial direction when the bolt head (53) is arranged within the tolerance compensation element (7).
22. The drive assembly of claim 21, wherein the slide bearing bushing (71) is configured to be slotted.
23. The drive assembly according to claim 22, wherein the slit (77) of the plain bearing bush (71) is configured to be inclined with respect to the axial direction of the plain bearing bush (71).
24. The drive assembly according to any one of claims 20 to 23,
-wherein the damping cap (72) has at least one sealing lip (72 a) on the radially outer side and
-wherein the at least one sealing lip (72 a) is configured such that when the tolerance compensating element (7) is arranged in the first wall opening (31 a), an axial form fit exists between the damping cap (72) and the first wall (31).
25. The drive assembly according to claim 24, wherein the damping cap (72) is configured such that the at least one sealing lip (72 a, 72 b) is pressed radially outwards when the bolt head (53) of the through bolt (5) is arranged within the tolerance compensation element (7).
26. The drive assembly according to any one of claims 20 to 25, wherein the slide bearing bushing (71) has a radially outwardly protruding catch lug (78) on at least one axial end.
27. The drive assembly according to any one of claims 1 to 17,
-wherein the through bolt (5) is fastened on the second wall (32),
wherein the through-bolts (5) clamp the two sleeves (41, 42) and the second wall (32) relative to each other,
-wherein the through bolt (5) is held on the first wall (31) by means of a holding element (55), and
-wherein the retaining element (55) secures the through bolt (5) to the first wall (31) in a radial direction.
28. The drive assembly according to claim 27,
-wherein the holding element (55) is screwed into an internal thread (31 f) of the wall opening (31 a) of the first wall (31) by means of an external thread (55 a),
wherein the holding element (55) has a holding opening (55 c) in which a bolt head (53) of the through-bolt (5) is held,
-wherein the holding opening (55 c) is configured to widen in a direction towards the second wall (32), and/or
-wherein the bolt head (53) of the through bolt (5) is configured to taper in a direction towards the first wall (31).
29. The drive assembly according to claim 27,
-wherein the holding element (55) is arranged in the wall opening (31 a) of the first wall (31),
-wherein the bolt head (53) of the through bolt (5) has an external thread (53 c),
-wherein the retaining element (55) is screwed onto the external thread (53 c) of the bolt head (53),
-wherein the holding element (55) has a side surface (55 b) tapering in a direction towards the second wall (32), and/or
-wherein the wall opening (31 a) of the first wall (31) is configured to taper in a direction towards the second wall (32).
30. The drive assembly according to any one of the preceding claims,
-wherein each sleeve (41, 42) has a compression zone (43 a) and
-wherein a press fit is configured between the compression zone (43 a) and the through-bore (20).
31. A drive assembly according to any of the preceding claims, wherein the through-going bore (20) centrally has a centering region (20 a) with a smaller inner diameter than the rest of the through-going bore (20) for centering the two sleeves (41, 42).
32. The drive assembly according to any one of the preceding claims, wherein the through bolt (5) is configured as a screw, and wherein the through bolt is screwed into an internal thread (32 a) of the second wall (32).
33. The drive assembly according to any one of claims 1 to 31,
-wherein the through-bolt (5) is configured as a screw, and
-wherein the through bolt (5) is screwed into a nut (51) arranged on the second wall (32).
34. The drive assembly according to claim 33, wherein the nut (51) is arranged torsionally resistant in a slot (32 b) of the second wall (32).
35. The drive assembly according to any one of claims 3 to 34,
-wherein the flange (44) of at least one sleeve (41, 42) has a thickness (41 h) substantially corresponding to the wall thickness (43 h) of the stem (43) of said sleeve (41, 42), or
-wherein the flange (44) of at least one sleeve (41, 42) has a thickness (41 h) corresponding to at least 1.5 times the wall thickness (43 h) of the stem (43) of said sleeve (41, 42).
36. Vehicle, in particular a vehicle, preferably an electric bicycle, which can be operated with muscle force and/or motor force, comprising a drive assembly (1) according to any of the preceding claims.
37. The vehicle according to claim 36, further comprising a chain wheel (106) connected with an output shaft (108) of the drive unit (2), and wherein the second wall (32) of the drive assembly (1) is arranged on a side of the chain wheel (106).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102022202102.9 | 2022-03-01 | ||
| DE102022206431.3 | 2022-06-27 | ||
| DE102022206431.3A DE102022206431A1 (en) | 2022-03-01 | 2022-06-27 | drive assembly |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116691906A true CN116691906A (en) | 2023-09-05 |
Family
ID=87830015
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202310188166.XA Pending CN116691906A (en) | 2022-03-01 | 2023-03-01 | Drive assembly and vehicle |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN116691906A (en) |
-
2023
- 2023-03-01 CN CN202310188166.XA patent/CN116691906A/en active Pending
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