阅读说明：本技术 用于电动车辆的驱动桥的门式驱动装置 (Door type driving device for driving axle of electric vehicle ) 是由 J·卢卡 P·伦茨 于 2021-04-29 设计创作，主要内容包括：本发明涉及一种用于电动车辆的具有驱动车轮的车桥的门式驱动装置,该门式驱动装置包括：具有驱动轴线(a)的驱动轴(AN)和具有从动轴线和车轮轴线(b)的从动轴(AB),其中驱动轴线(a)和从动轴线(b)具有轴线偏移或门式偏移(c),其中在驱动轴(AN)与从动轴(AB)之间布置有第一传动级本发明提出：在轴向方向上在第一传动级旁边布置有第二传动级并且在第二传动级旁边布置有切换装置(SE)；并且能够借助于切换装置(SE)来切换第一传动级和第二传动级(The invention relates to a portal drive for an electric vehicle having an axle for driving wheels, comprising: a drive shaft (AN) having a drive axis (a) and a driven shaft (AB) having a driven axis and a wheel axis (b), wherein the drive axis (a) and the driven axis (b) have AN axis offset or a portal offset (c), wherein at the drive shaftA first transmission stage is arranged between the (AN) and the output shaft (AB) The invention proposes: in the axial direction in the first gear stage A second transmission stage is arranged beside And in the second gear stage A switching device (SE) is arranged beside the switching device; and the first transmission stage can be switched by means of a switching device (SE) And a second gear stage)

1. A portal drive apparatus for an electric vehicle having an axle that drives wheels, the portal drive apparatus comprising: a drive shaft (AN) having a drive axis (a) and a driven shaft (AB) having a driven axis and a wheel axis (b), whereinThe drive axis (a) and the driven axis (b) have AN axis offset or a portal offset (c), wherein a first gear stage is arranged between the drive shaft (AN) and the driven shaft (AB)Characterized in that in the axial direction in the first transmission stageA second transmission stage is arranged besideAnd in said second transmission stageA switching device (SE) is arranged beside the switching device; and the first transmission stage can be switched by means of the switching device (SE)And said second transmission stage

2. The portal drive of claim 1, wherein the first gear stageAnd said second transmission stageEach having a drive gear (Z1, Z3), a driven gear (Z2, Z4) and two intermediate gears (ZR1, ZR2, ZR3, ZR4), wherein the drive gear (Z1, Z3) is designed as a fixed gear on the drive shaft (AN) and the driven gear (Z2, Z4) is designed as AN idler gear on the driven shaft (AB).

3. The portal drive of claim 2, wherein the second gear stageIs rotatably arranged in the first transmission stageOn the driven gear (Z2).

4. The portal drive of claim 3, wherein the first gear stageHas a neck (12), and the second transmission stageIs supported on the neck (12).

5. Door drive according to claim 3 or 4, characterized in that the first gear stageHas a first synchronizing tooth (15), and the second transmission stageHas second synchronizing teeth (16); the switching device (SE) comprises a sliding sleeve (17) having corresponding synchronization teeth (17a, 17 b); and can be switched to a first or second gear by means of a toothing engagement between the first or second synchronization tooth (15, 16) and a corresponding synchronization tooth (17a, 17b) of the sliding sleeve (17).

6. Door drive according to claim 5, characterized in that the switching means (SE) can be actuated hydraulically or pneumatically.

7. The portal drive according to claim 6, characterized in that the switching device (SE) has an axially displaceable hydraulic piston (19) which is coupled with the sliding sleeve (17).

8. Portal drive device according to claim 5, 6 or 7, characterized in that the sliding sleeve (17) is arranged on the driven shaft (AB) in a rotationally fixed, yet axially displaceable manner.

9. Door-type drive according to one of the claims 1 to 8, characterized in that the driven shaft (AB) is connected in an actively driving manner with a planetary gear set (PS).

10. Door drive according to claim 9, characterized in that the planetary gear set (PS) has a sun Shaft (SO) which can be driven by the driven shaft (AB), a fixed ring gear shaft (HR) and a driven planet carrier Shaft (ST).

11. Portal drive according to claim 9, characterized in that the planet carrier Shaft (ST) is integrated into a hub (6) driving a wheel.

12. Portal drive arrangement according to one of claims 1 to 11, characterized in that the axle has a housing (3) and a hub support (4); and the first transmission stageAnd said second transmission stageAnd with a liquidThe switching device (SE) of the pressure piston (19) is arranged within the housing (3) and the hub support (4).

Technical Field

The invention relates to a portal drive for an electric vehicle having a drive axle for driving wheels, comprising: a drive shaft having a drive axis and a driven shaft having a driven or wheel axis, wherein the drive axis and the driven axis have an axis offset or a portal offset, and wherein a first transmission stage is arranged between the drive shaft and the driven shaft.

Background

Portal drives for axles are known, which have a so-called portal offset, i.e. an offset between the drive axis (generally the half-shaft of an axle differential) and the wheel axis. This results in either a greater ground clearance of the vehicle (i.e. the drive axis is higher than the wheel axis) or a smaller ground clearance (in particular in low-floor vehicles with wheel axes higher than the drive axis).

A gate drive (also referred to as a gate drive) having a planetary gear whose ring gear has an internal and an external toothing is known from DE 102004003649 a 1. The drive device is constituted by a sun gear or a sun shaft, and realizes output by a driven gear that engages with external teeth of the ring gear. The axes of the sun shaft and the driven gear have vertical and horizontal axis offsets (portal offset).

A further embodiment of a portal drive is known from DE 3027806C 2, namely a drive axle for a bus. The portal drive is driven by the half shafts of an axle differential, which is arranged eccentrically on the axle. The portal drive comprises a drive gear driven by the axle shafts and a driven gear arranged vertically above the drive gear, the axis of the driven gear corresponding to the wheel axis. Two intermediate gears are arranged symmetrically between the drive gear and the driven gear, which intermediate gears are each in toothed engagement with the drive gear and the driven gear. Such known portal drives have a vertical portal offset, wherein the wheel axis is arranged above the drive axis, and are therefore particularly suitable for low-floor vehicles.

A problem in known axles driven by an electric machine is that: the achievable speed range is too small or the available drive torque or tractive force at the drive axle is too small.

Disclosure of Invention

The object of the invention is to achieve a sufficiently high final speed and a sufficiently good climbing behavior of the vehicle in an electrically driven axle with a portal drive, i.e. in a portal axle, in particular for low-floor vehicles.

According to the invention, the portal drive has two gear stages, namely portal gear stages designed with an axis offset or portal offset, which are arranged next to one another and can be shifted by means of a shifting device. The following advantages are thereby achieved: by means of the portal drive according to the invention, two gears can be shifted, as a result of which, on the one hand, a higher final speed can be achieved in the second gear and, on the other hand, a higher tractive force can be achieved in the first gear. The shifting device is arranged in the immediate vicinity of the two gear stages, i.e. outside the two gear stages rather than inside the two gear stages. This results in a compact design of the portal drive. An electric vehicle is understood to mean a vehicle, in particular a low-floor vehicle, which is driven exclusively electrically, for example by one or more electric machines, or has a hybrid drive, which has a combustion engine and an electric machine.

According to a preferred embodiment, the two gear stages or portal gear stages each have a drive gear, a driven gear and intermediate gears which are in toothed engagement with the drive gear and the driven gear. This results in a portal offset on the one hand and a power split by the two intermediate gears on the other hand. The driving gear is designed as a fixed gear and the driven gear is designed as an idler gear which is rotatably arranged on the driven shaft.

According to a further preferred embodiment, the driven gear of the second transmission stage (second driven gear) is rotatably arranged on the driven gear of the first transmission stage (first driven gear). The following advantages are thereby achieved: the first driven gear and the second driven gear can be easily coupled with the switching device disposed beside the second driven gear. This saves installation space in the axial direction.

According to a further preferred embodiment, the driven gearwheel of the first transmission stage has a neck which serves as a bearing base for the driven gearwheel of the second transmission stage. At the same time, the connection to the switching device is provided by a neck which is designed as a hollow shaft and transmits the torque.

According to a further preferred embodiment, the first driven gear has a first synchronizing tooth and the second driven gear has a second synchronizing tooth, while the switching device has a sliding sleeve with a corresponding synchronizing tooth. Thereby realizing that: the first or second synchronization tooth can mesh with a corresponding synchronization tooth of the sliding sleeve. It is thus possible to switch to the first gear and the second gear.

According to a further preferred embodiment, the switching device can be actuated hydraulically or pneumatically. The sliding sleeve is displaced by a switching force generated by means of hydraulic or pneumatic pressure into its respective switching position.

According to a further preferred embodiment, the switching device has an axially displaceable hydraulic piston to which the hydraulic medium is applied and which is kinematically coupled with the sliding sleeve. The movement of the hydraulic piston in the axial direction is thus transmitted to the sliding sleeve, which causes the engagement or disengagement of the idler gear.

According to a further preferred embodiment, the sliding sleeve is arranged on the driven shaft in a rotationally fixed, yet axially displaceable manner. Preferably, this arrangement may be achieved by means of synchronizing or wedge teeth. Thus, the torque of the idler gear can be transmitted to the driven shaft via the sliding sleeve.

According to a further preferred embodiment, the output shaft is connected in an actively driving manner to a planetary gear set (referred to as planetary set for short). Preferably, the output shaft of the portal drive drives the sun shaft of the planetary set, wherein the ring gear shaft of the planetary set is held stationary, i.e. supported on the housing side. The planetary set is output to the driving wheels of the vehicle by the planet carrier shaft of the planetary set.

According to a further preferred embodiment, the driven planet carrier shaft of the planetary set is integrated into the hub of the drive wheel, i.e. the planet carrier shaft is part of the hub and thus drives the drive wheel.

According to a further preferred embodiment, the axle has a housing and a hub carrier which is fixedly connected to the housing, the two transmission stages or portal transmission stages and the shifting device with the hydraulic piston being arranged in the housing and the hub carrier. The portal drive can thus be placed compactly and close to the wheel in the housing and the hub support.

Drawings

An embodiment of the invention is shown in the drawings and will be described in more detail below, wherein other features and/or advantages may be derived from the description and/or drawings. In the drawings:

figure 1 shows a transmission diagram of a portal drive according to the invention for an electrically drivable axle,

figure 2 shows a constructive embodiment of the portal drive according to the transmission diagram of figure 1,

figure 3 shows an enlarged partial cross-section of a portal drive with a switching device,

figure 4 shows an axial section in the region of the intermediate gear of the portal drive,

fig. 5 shows a view in the axial direction towards the first transmission stage with intermediate gear wheels, and

fig. 6 shows a view of the second transmission stage with intermediate gear wheels.

Detailed Description

Fig. 1 shows a transmission diagram 1, namely a schematic representation of a portal drive PO according to the invention and a planetary gear set PS which can be driven by the portal drive PO. The portal drive PO is preferably used for driving an electric vehicle, in particular for driving an electrically driven low floor vehicle. The gate drive device PO includes: a drive shaft AN having a drive axis a; and a driven shaft AB having a driven axis b coincident with the wheel axis b. The drive axis a and the driven axis b, which is arranged in the figures and in the vehicle above the drive axis a, have an axis distance c, also referred to as an axis offset or portal offset c. The drive shaft AN may be driven by the half shafts of AN axle differential of the vehicle (not shown). The portal drive PO has two gear stages, namely a first gear stageAnd a second gear stageThese gear stages can be switched by means of a switching device SE. First gear stageWith a first gear Z1 (also referred to as fixed gear Z1) arranged in a rotationally fixed manner on the drive shaft AN and a second gear Z2 (also referred to as idler gear Z2) arranged rotatably on the driven shaft AB. As can be seen from the figures, the first gear Z1 and the second gear Z2 are not in toothed engagement with one another in the plane of the drawing, but a gap S1 remains between the two gears Z1, Z2. The power transmission from the driving first gear Z1 to the driven second gear Z2 is effected by means of two intermediate gears arranged in front of and behind the plane of the drawing, which are in toothed engagement with the first gear Z1 and the second gear Z2; thereby achieving a distribution of power flow. Fig. 5 shows the first gear stage with the intermediate gears ZR1, ZR2 in the axial directionAnd will be explained in detail there. Second gear stageWith a third gear Z3 (also referred to as fixed gear Z3) arranged in a rotationally fixed manner on the drive shaft AN and a fourth gear Z4 (also referred to as idler gear Z4) arranged rotatably relative to the second gear Z2. In the first gear stageSimilarly, the driving third gear Z3 and the driven fourth gear Z4 are not in direct tooth engagement with one another, but rather leave a gap S2 between the two gears Z3, Z4 in the plane of the drawing. Analogous to the first gear stageIn the second gear stageAlso by means of intermediate gears ZR3, ZR4 arranged in front of and behind the plane of the drawing, which intermediate gears are shown and described in fig. 6. By means of a switching device SE having a sliding sleeve (not numbered) which can be displaced in the axial direction, the drive shaft AN can be passed through the first transmission stageOr a second gear stageConnected with the driven shaft AB. Upon switching to the first gear stageWhen the sliding sleeve is in the shift position A, the sliding sleeve is shifted to the second gear stageWhen in the switching position B, the sliding sleeve is in the switching position B. By means of a sliding sleeve, in the second gear Z2Or fourth gear Z4, and the driven shaft AB. In neutral position N, which is arranged between these two shift positions A, B, no torque is transmitted between drive input shaft AN and output shaft AB. It should be noted that the switching device SE is not located between the idle gears Z2, Z4, but outside these, i.e. adjacent to the fourth gear Z4, which is supported on the hollow shaft (no reference numeral) of the second gear Z2. The planetary gear set PS has a sun shaft SO, a carrier shaft ST, a housing-side supported ring gear shaft HR, and planetary gears PL supported on the carrier shaft ST, which mesh with the sun gear of the sun shaft SO and the ring gear of the ring gear shaft HR. The planetary gear set PS is driven by the driven shaft AB of the portal drive PO via the sun shaft SO. The planetary gear set PS achieves output via a carrier shaft ST, which may be integrated into the rim (Radkopf) of the driving wheel of the vehicle.

Fig. 2 shows a structural embodiment 2 of the transmission diagram 1 according to fig. 1. The same reference numerals are used for functionally identical or similar components. The drive shaft AN (on which the fixed gears Z1, Z3 are arranged) has AN axis offset or portal offset c with respect to the driven shaft AB (on which the idler gears Z2, Z4 are supported), wherein the drive axis a is arranged in the drawing and also in the vehicle below the driven shaft or wheel axis b. The gear pairs Z1, Z2 form the first gear stage of the portal drive POAnd the gear pair Z3, Z4 forms a second gear stageThe two transmission stages are switched by a switching device SEThe portal drive PO is shown enlarged in fig. 3, 4 and described in detail there. The output shaft AB is mounted in the housing 3 and the hub carrier 4 and is connected on the end side to the sun shaft SO of the planetary gear set PS in a rotationally fixed manner. A sun gear 5 is arranged on the sun shaft SO. IntegrationThe planet carrier shaft ST into the wheel rim or hub 6 has planet journals 7 on which the planet gears PL are supported. The ring gear shaft HR is supported against rotation relative to the hub support 4. The hub 6 (in which the planetary sets PS are accommodated) is supported relative to the hub support 4 by means of tapered roller bearings 8. A drive wheel, not shown, of the electric vehicle is fastened to the hub 6 by means of wheel bolts 9. The brake disk 10 is connected to the hub 6 in a rotationally fixed manner.

Fig. 3 shows an enlarged illustration of the portal drive PO already illustrated in fig. 2. The same reference numerals are used for the same components. The driven shaft AB is supported at an end side with respect to the housing 3 by a cylindrical roller bearing 11. An idler gear Z2 with a neck 12 designed as a hollow shaft is supported on the output shaft AB by means of a needle bearing 13 relative to the output shaft AB. The idler gear Z4 is supported on the neck 12 of the idler gear Z2 by means of a further needle bearing 14. The neck 12 of the idler gear Z2 has first synchronisation teeth 15 (external teeth) and the idler gear Z4 has second synchronisation teeth 16 (internal teeth). The shift device SE comprises a sliding sleeve 17 which is arranged on the output shaft AB so as to be rotationally fixed, but axially displaceable, by means of an internal toothing 17a designed as a synchronizing tooth and has an external toothing 17b designed as a synchronizing tooth. The sliding sleeve 17 is in the illustration according to fig. 3 in a neutral position, in which the sliding sleeve 17 is held by a fixing pin 18. In the neutral position, no torque is transmitted. The sliding sleeve 17 is actuated by a hydraulic piston 19 which is arranged in the cylinder bore 20 so as to be axially displaceable, i.e. to move to two switching positions A, B (fig. 1). The hydraulic piston 19 has a first, larger piston surface 19a and a second, smaller piston surface 19b, to which a pressure medium, preferably a hydraulic fluid, can be applied.

For shifting to first gear (i.e. first gear stage)) The sliding sleeve 17 (also referred to as the shifting sleeve 17) is displaced to the right in the drawing by the hydraulic piston 19, so that the internal teeth 17a of the sliding sleeve 17 engage the external teeth 15 of the idler gear Z2 and an anti-rotating form-fitting connection is established. For switching to second gear (i.e. second gear)Dynamic stage) The switching sleeve 17 is shifted leftward in the drawing beyond the neutral position so that the external teeth 17b of the switching sleeve 17 engage the internal teeth 16 of the idler gear Z4.

FIG. 4 shows the drive axis a, the first gear stageOf the intermediate gears ZR1, ZR2, and the axes m1, m2 of the second transmission stageIs the intermediate gear ZR3, ZR4, in axial section in the plane of the axes m3, m 4. In the plane of the drawing, the first gear Z1 is in toothed engagement with the first intermediate gear ZR1 and the second intermediate gear ZR 2; the third gear Z3 is in toothed engagement with the two intermediate gears ZR3, ZR 4.

Fig. 5 shows the direction from the drive shaft AN towards the first transmission stageHas a driving first gear Z1, two intermediate gears ZR1, ZR2 and a driven second gear Z2. From this illustration, the power from the first driving gear Z1 is distributed to the two intermediate gears ZR1, ZR2 and is transmitted from these two intermediate gears to the second driven gear Z2. Due to this power distribution, the teeth and bearings are subjected to less stress.

FIG. 6 shows a 3D representation similar to FIG. 5, however oriented toward the second gear stageThis second transmission stage is formed by a third driven gear Z3, two intermediate gears ZR3, ZR4 and a fourth driven gear Z4. In comparison with fig. 5, the first gear stage is clearly visibleAnd the second transmissionStageDifferent diameter ratios of (a).

List of reference numerals

1 drive schematic

2 structural embodiment

3 case

4 hub support

5 Sun gear

6 wheel hub

7 planetary journal

8 tapered roller bearing

9 wheel bolt

10 brake disc

11 cylindrical roller bearing

12 neck of the second gear

13 needle roller bearing

14 needle roller bearing

15 first synchronous tooth (Z2)

16 second synchronizing tooth (Z4)

17 sliding sleeve/switching sleeve

17a synchronous internal teeth

17b synchronous external teeth

18 fixed pin

19 Hydraulic piston

19a first piston face

19b second piston face

20 cylinder hole

A first switching position

a drive axis

AB driven shaft

AN drive shaft

B second switching position

b driven and wheel axes

c door type offset

HR ring gear shaft

m1 Axis (ZR1)

m2 Axis (ZR2)

m3 Axis (ZR3)

m4 Axis (ZR4)

N neutral position

PL planetary gear

PO gate type driving device

PS planetary gear set

S1 gap

S2 gap

SE switching device

SO sun shaft

ST planet carrier shaft

First gear stage

Second gear stage

Z1 first Gear (fixed gear)

Z2 second Gear (idler gear)

Z3 third Gear (fixed gear)

Z4 fourth Gear (idler gear)

ZR1 first intermediate gear

ZR2 second intermediate gear

ZR3 third intermediate gear

ZR4 fourth intermediate gear