DE102015004051B4 - Gear arrangement of a drive for a twin-screw extruder - Google Patents

Abstract

Gear arrangement (10; 30) of a drive for a twin-screw extruder, with a power distribution stage (11; 31) and with a power summation stage (12; 32), the power distribution stage (11; 31) having gear wheels (13, 14, 15; 33, 34, 35), and wherein the power summation stage (12; 32) also has gears (16, 17, 18; 36, 37, 38) meshing with one another, characterized in that the gears (13, 14, 15) of the power distribution stage ( 11) single helical and the gears (16, 17, 18) of the power summation stage (12) are double helical and those positioned on a second output shaft (22) as well as those on a first branch shaft (20) and those on a second branch shaft (21). double helical gears (16, 17, 18) each having toothing sections (16a, 16b, 17a, 17b, 18a, 18b) which have helix angles with opposite directions of inclination and different amounts, or that the Gears (33, 34, 35) of the power distribution stage (31) have double helical gears and the gears (36, 37, 38) of the power summation stage (32) have single helical gears and the gears on a first output shaft (39) as well as those on a first branch shaft (40 ) and the double helical gears (33, 34, 35) positioned on a second branch shaft (41) each have toothing portions (33a, 33b, 34a, 34b, 35a, 35b) having helix angles with opposite directions of inclination and different amounts.

Description

The invention relates to a gear arrangement of a drive for a twin-screw extruder according to the preamble of claim 1. The invention also relates to a drive for a twin-screw extruder with such a gear arrangement.

From the DE 10 2004 051 306 B4 the basic structure of a drive device for a twin-screw extruder and a gear arrangement of such a drive device is known, which interacts with the output shafts of the drive device. It is known from this prior art that the transmission arrangement interacting with the output shafts of the drive device comprises a power distribution stage and a power summation stage. The power distribution stage has intermeshing gears, and the power summation stage has intermeshing gears. The gears of the power distribution stage and the gears of the power summation stage are each designed as single helical gears.

If the gear arrangement of the drive device of a twin-screw extruder has to transmit higher outputs and torques, this can be realized according to the prior art by adapting the size of the gear arrangement. However, an increasing increase in the power or torque to be transmitted can no longer be realized by simply enlarging the previous design of the transmission arrangement. There is therefore a need for a new type of gear arrangement for a drive of a twin-screw extruder, with the aid of which higher outputs or torques can be transmitted compared to the gear arrangements known from the prior art.

Proceeding from this, the object of the present invention is to create a novel gear arrangement of a drive for a twin-screw extruder and a drive for a twin-screw extruder with such a gear arrangement.

This object is achieved by a transmission arrangement according to claim 1.

According to the invention, the gears of the power distribution stage are single helical and the gears of the power summation stage are double helical, or the gears of the power distribution stage are double helical and the gears of the power summation stage are single helical. As a result, greater power and torque can be transmitted by the gear arrangement. The double helical gears each have toothing sections that have helix angles with opposite directions of inclination and different amounts.

According to an advantageous development, the power distribution stage has a first gear wheel positioned on a first output shaft, a second gear wheel positioned on a first branch shaft, and a third gear wheel positioned on a second branch shaft, the gear wheels of the power distribution stage having single helical teeth, and the second gear wheel and the third gear mesh in each case with the first gear. The power summing stage has a fourth gear positioned on a second output shaft, a fifth gear positioned on the first branch shaft and a sixth gear positioned on the second branch shaft, the gears of the power summing stage being double helical, and the fifth gear and sixth gear respectively in mesh the fourth gear. This configuration is particularly preferred for the transmission of greater power and torque.

Preferably, the double helical gears positioned on the second output shaft as well as those positioned on the first branch shaft and the second branch shaft each have gear portions having helix angles with opposite directions of inclination and different amounts. The amounts of the helix angles running in opposite directions of inclination deviate from one another in such a way that there is a balance of forces on the shafts with regard to the forces resulting from the gearing. As a result, axial forces acting on the transmission arrangement, which result from the toothing, can be compensated.

The drive according to the invention for a twin-screw extruder is defined in claim 8.

• 1: eine erfindungsgemäße Getriebeanordnung eines Antriebs für einen Doppelschneckenextruder; und
• 2 eine weitere erfindungsgemäße Getriebeanordnung eines Antriebs für einen Doppelschneckenextruder.

Preferred developments of the invention result from the dependent claims and the following description. Exemplary embodiments of the invention are explained in more detail with reference to the drawing, without being limited thereto. It shows:

• 1 : a gear arrangement according to the invention of a drive for a twin-screw extruder; and
• 2 another gear arrangement according to the invention of a drive for a twin-screw extruder.

The invention relates to a gear arrangement of a drive for a twin-screw extruder and a drive for a twin-screw extruder which includes such a gear arrangement.

The construction of a drive for a twin-screw extruder is familiar to the person skilled in the art addressed here and from DE 10 2004 051 306 B4 known.

Thus, a drive for a twin-screw extruder comprises at least one motor, each motor acting on a drive shaft. Furthermore, the drive of a twin-screw extruder comprises a plurality of output shafts, with a screw shaft of the twin-screw extruder being coupled to each output shaft. A gear arrangement and a second gear arrangement designed as a power split gear are connected between the or each drive shaft and the output shafts.

The present invention relates to a gear arrangement designed as a power-dividing gear for such a drive of a twin-screw extruder.

1 12 shows a preferred exemplary embodiment of a gear arrangement 10 designed as a power split gear for a drive of a twin-screw extruder, the gear arrangement 10 comprising a power distribution stage 11 and a power summation stage 12 . The power distribution stage 11 includes intermeshing gears 13, 14 and 15. The power summing stage 12 also has intermeshing gears 16, 17 and 18.

In the preferred exemplary embodiment shown, gear wheel 13 of power distribution stage 11 is positioned on a first output shaft 19, which is used to drive a first screw shaft of a twin-screw extruder, with the first screw shaft of the twin-screw extruder being able to be coupled to this first output shaft 19. Gear 14 of power distribution stage 11 and gear 15 of power distribution stage 11 are each positioned on branch shafts, namely gear 14 on a first branch shaft 20 and gear 15 on a second branch shaft 21.

The gear wheel 16 of the power summation stage 12 is positioned on a second output shaft 22 to which a second screw shaft of the twin-screw extruder can be coupled. Gears 17 and 18 of power summation stage 12, which mesh with gear 16, are in turn positioned on the branch shafts, namely gear 17 of power summation stage 12 on the first branch shaft 20 and gear 18 of power summation stage 12 on the second branch shaft 21.

In the preferred embodiment shown, the meshing gears 13, 14 and 15 of the power distribution stage 11 are single helical and the gears 16, 17 and 18 of the power summing stage 12 are double helical. So can 1 It can be seen that each of the gears 16, 17 and 18 of the power summation stage 12 has two toothed sections 16a, 16b or 17a, 17b or 18a, 18b, the toothed sections 17a, 18a of the gears 17, 18 fitting into the toothed section 16a of the gear 16 and the toothed portions 17b, 18b of the gears 17, 18 mesh in the toothed portion 16b of the gear 16. The meshing toothed sections 16a, 17a, 18a have opposite the meshed toothed sections 16b, 17b, 18b, related to the respective gear wheel 16, 17, 18, helix angles with opposite directions of inclination and different amounts. Thus, the inclination directions of the toothed portions 16a, 16b of the gear 16, the toothed portions 17a, 17b of the gear 17 and the toothed portions 18a, 18b of the gear 18 are respectively provided with helix angles having opposite helix directions and different amounts.

$$\text{F}14=\left(\text{F}17\text{a}-\text{F}17\text{b}\right)$$

$$\text{F}13=\left(\text{F}15+\text{F}14\right)=\left(\text{F}16\text{a}+\text{F}16\text{b}\right)$$

The amounts of the helix angles of the toothed sections 16a, 16b or 17a, 17b or 18a, 18b of the respective gear wheels 16, 17, 18 running in opposite directions of inclination differ from one another in such a way that there is a balance of forces on the shafts 19, 22, 21, 20 with regard to the (axial) forces resulting from the gearing, namely the following absolute force balances: $$\text{<figure-callout id="15" label="f" filenames="DE102015004051B4\_0006.png" state="{{state}}">f</figure-callout>}15=\left(\text{f}18\text{a}-\text{<figure-callout id="18b" label="f" filenames="DE102015004051B4\_0006.png" state="{{state}}">f</figure-callout>}18\text{b}\right)$$

$$\text{<figure-callout id="14" label="f" filenames="DE102015004051B4\_0006.png" state="{{state}}">f</figure-callout>}14=\left(\text{<figure-callout id="17a" label="f" filenames="DE102015004051B4\_0006.png" state="{{state}}">f</figure-callout>}17\text{a}-\text{<figure-callout id="17b" label="f" filenames="DE102015004051B4\_0006.png" state="{{state}}">f</figure-callout>}17\text{b}\right)$$

$$\text{<figure-callout id="13" label="f" filenames="DE102015004051B4\_0006.png" state="{{state}}">f</figure-callout>}13=\left(\text{<figure-callout id="15" label="f" filenames="DE102015004051B4\_0006.png" state="{{state}}">f</figure-callout>}15+\text{f}14\right)=\left(\text{<figure-callout id="16a" label="f" filenames="DE102015004051B4\_0006.png" state="{{state}}">f</figure-callout>}16\text{a}+\text{<figure-callout id="16b" label="f" filenames="DE102015004051B4\_0006.png" state="{{state}}">f</figure-callout>}16\text{b}\right)$$

$$\text{tan}\left(\mathrm{\beta }15\right)/\text{d}15=\left(\text{tan}\left(\mathrm{\beta }18\text{a}\right)-\text{tan}\left(\mathrm{\beta }18\text{b}\right)\right)/\text{d}18$$

wobei β14 der Schrägungswinkel des Zahnrads 14 ist, wobei β17a der Schrägungswinkel des Verzahnungsabschnitts 17a des Zahnrads 17 und β17b der hierzu gegenläufige Schrägungswinkel des Verzahnungsabschnitts 17b des Zahnrads 17 ist, wobei β15 der Schrägungswinkel des Zahnrads 15 ist, wobei β18a der Schrägungswinkel des Verzahnungsabschnitts 18a des Zahnrads 18 und β18b der hierzu gegenläufige Schrägungswinkel des Verzahnungsabschnitts 18b des Zahnrads 18 ist, wobei d17 der Teilkreisdurchmesser der beiden Verzahnungsabschnitte 17a, 17b des Zahnrads 17 auf der Zweigwelle 20 ist, und wobei d18 der Teilkreisdurchmesser der beiden Verzahnungsabschnitte 18a, 18b des Zahnrads 18 auf der Zweigwelle 21 ist. Entsprechend ist d14 der Teilkreisdurchmesser des Zahnrades 14 und d 15 der des Zahnrades 15.The above balances of forces can be realized particularly advantageously by the following relationships applying: $$\text{tan}\left(\mathrm{\beta }14\right)/\text{i.e}14=\left(\text{tan}\left(\mathrm{<figure-callout\; id="17a"\; label="\beta "\; filenames="DE102015004051B4\_0006.png"\; state="\{\{state\}\}">\beta </figure-callout>}17\text{a}\right)-\text{tan}\left(\mathrm{<figure-callout\; id="17b"\; label="\beta "\; filenames="DE102015004051B4\_0006.png"\; state="\{\{state\}\}">\beta </figure-callout>}17\text{b}\right)\right)/\text{i.e}17$$

$$\text{tan}\left(\mathrm{\beta }15\right)/\text{i.e}15=\left(\text{tan}\left(\mathrm{\beta }18\text{a}\right)-\text{tan}\left(\mathrm{<figure-callout\; id="18b"\; label="\beta "\; filenames="DE102015004051B4\_0006.png"\; state="\{\{state\}\}">\beta </figure-callout>}18\text{b}\right)\right)/\text{i.e}18$$

where β14 is the helix angle of the gear 14, where β17a is the helix angle of the gear 17a of the gear wheel 17 and β17b is the opposite helix angle of the toothed section 17b of the gear wheel 17, where β15 is the helix angle of the gear wheel 15, where β18a is the helix angle of the toothed section 18a of the gear wheel 18 and β18b is the opposite helix angle of the toothed section 18b of the gear wheel 18 is, where d17 is the pitch circle diameter of the two toothed sections 17a, 17b of the gear 17 on the branch shaft 20, and where d18 is the pitch circle diameter of the two toothed sections 18a, 18b of the gear 18 on the branch shaft 21. Correspondingly, d14 is the pitch circle diameter of gear 14 and d15 is that of gear 15.

Due to the different helix angles of the toothed sections 16a, 16b or 17a, 17b or 18a, 18b, different axial forces arise with the same transmitted torque. The above conditions or equations can be used to ensure that the amount of the difference in the axial forces on the toothed sections 17a, 17b or 18a, 18b of the gear wheel 17 or 18 corresponds to the amount of the axial force on the gear wheel 14 or 15.

Deviations from the exact fulfillment of the above conditions or equations result in different forces, which can be compensated for by adapted tooth widths of the toothed sections 17a, 17b or 18a, 18b.

in 1 In the preferred exemplary embodiment shown, the gear arrangement 10 designed as a power dividing gear has the power distribution stage 11 and the power summation stage 12, with the gears 13, 14 and 15 of the power distribution stage 11 having single helical teeth and the gears 16, 17 and 18 of the power summation stage 12 having double helical teeth. Each of the gears 16, 17 and 18 of the power summation stage 12 has toothed sections 16a, 16b or 17a, 17b or 18a, 18b with helix angles β, which have different directions of inclination and different amounts.

In contrast to this, it is also possible that the gear wheels of the power distribution stage have double helical gearing and the gear wheels of the power summation stage have single helical gearing. So shows 2 an exemplary embodiment of a transmission arrangement 30 designed as a power split transmission, which in turn comprises a power distribution stage 31 and a power summation stage 32, the power distribution stage 31 having the meshing gears 33, 34 and 35 and the power summation stage 32 having the meshing gears 36, 37 and 38. The gear 33 of the power distribution stage 31, which is double-helical and has the two toothed sections 33a and 33b, is positioned on a first output shaft 39, to which the first screw shaft of the twin-screw extruder can be coupled. The gears 34 and 35 of the power distribution stage 31, which are also double-helical and have the toothed sections 34a, 34b or 35a, 35b, are arranged on the branch shafts 40, 41, namely the gear 34 with the toothed sections 34a, 34b on the first branch shaft 40 and the gear 35 with the toothed portions 35a, 35b on the second branch shaft 41. In the variant of 2 the gears 36, 37 and 38 of the power summation stage 32 are designed with single helical teeth.

In the embodiment of 2 the toothed sections 33a, 33b or 34a, 34b or 35a, 35b of the respective gearwheels 33, 34 or 35 differ in terms of their angle of inclination in such a way that in relation to each gearwheel 33, 34 or 35 the respective toothed sections 33a, 33b or 34a, 34b or 35a, 35b each have helix angles with opposite directions of inclination and different amounts, with the amounts of the helix angles running in opposite directions of inclination deviating from one another in such a way that on the shafts 39, 40, 41, 42 or on the gear arrangement 30 there is a balance of forces with regard to the forces resulting from the gearing. The relevant in connection with the embodiment of 1 Conditions or equations described apply analogously to the embodiment of FIG 2 .

The gear arrangement according to the invention makes it possible to transmit greater power and torque for driving the screw shafts of a twin-screw extruder, one of the screw shafts of the twin-screw extruder being able to be coupled to each of the output shafts of the respective gear arrangement 10 or 30 . The first output shaft 19 or 39 of the respective transmission arrangement 10 or 30 can also be coupled to at least one motor on the drive side, in particular with the interposition of a planetary gear arrangement between the transmission arrangement 10 or 30 according to the invention and the motor. The drive power provided by the motors therefore reaches the first output shaft 19, 39 of the gear arrangements 10, 30 via the planetary gear arrangement (not shown) and, starting from the first output shaft 19, 39, via the branch shafts 20, 21 or 40, 41 in the direction of the respective second output shaft 22, 42 of the respective transmission arrangement 10 or 30.

Reference List

10

gear arrangement

11

power distribution level

12

power summation level

13

gear

14

gear

d14

Pitch circle of gear 14

15

gear

16

gear

17

gear

d17

Pitch circle of gear 17

18

gear

d18

Pitch circle of gear 18

19

output shaft

20

branch wave

21

branch wave

22

output shaft

30

gear arrangement

31

power distribution level

32

power summation level

33

gear

34

gear

35

gear

36

gear

37

gear

38

gear

39

output shaft

40

branch wave

41

branch wave

42

output shaft

Claims (8)

Gear arrangement (10; 30) of a drive for a twin-screw extruder, with a power distribution stage (11; 31) and with a power summation stage (12; 32), the power distribution stage (11; 31) having gear wheels (13, 14, 15; 33, 34, 35), and wherein the power summation stage (12; 32) also has gears (16, 17, 18; 36, 37, 38) meshing with one another, characterized in that the gears (13, 14, 15) of the power distribution stage ( 11) single helical and the gears (16, 17, 18) of the power summation stage (12) are double helical and those positioned on a second output shaft (22) as well as those on a first branch shaft (20) and those on a second branch shaft (21). double helical gears (16, 17, 18) each having toothing sections (16a, 16b, 17a, 17b, 18a, 18b) which have helix angles with opposite directions of inclination and different amounts, or that di e gears (33, 34, 35) of the power distribution stage (31) have double helical gears and the gears (36, 37, 38) of the power summation stage (32) have single helical gears and the ones on a first output shaft (39) as well as those on a first branch shaft ( 40) and the double helical gears (33, 34, 35) positioned on a second branch shaft (41) each have toothed sections (33a, 33b, 34a, 34b, 35a, 35b) having helix angles with opposite directions of inclination and different amounts. Gear arrangement according to claim 1 , characterized in that the power distribution stage (11) has a first gear (13) positioned on the first output shaft (19), a second gear (14) positioned on the first branch shaft (20), and a third gear positioned on the second branch shaft (21). Gear (15), wherein the gears of the power distribution stage (11) are single helical, and wherein the second gear (14) and the third gear (15) each mesh with the first gear (13). Gear arrangement according to claim 1 or 2 , characterized in that the power summation stage (12) has a fourth gear (16) positioned on the second output shaft (22), a fifth gear (17) positioned on the first branch shaft (20) and a sixth gear positioned on the second branch shaft (21). Gear (18), wherein the gears of the power summation stage (12) are double helical, and wherein the fifth gear (17) and the sixth gear (18) each mesh with the fourth gear (16). Transmission arrangement according to one of Claims 1 until 3 , characterized in that the amounts of the helix angles running in opposite directions of inclination deviate from one another in such a way that there is a balance of forces on the shafts with regard to the axial forces resulting from the toothing. Gear arrangement according to claim 1 , characterized in that the power split stage (31) has a first gear (33) positioned on a first output shaft (39), a second gear (34) positioned on a first branch shaft (40), and a second gear (34) on a second branch shaft (41) positioned third gear (35), wherein the gears of the power distribution stage (31) are double helical, and wherein the second gear (34) and the third gear (35) mesh with the first gear (33). Gear arrangement according to claim 5 , characterized in that the power summation stage (32) has a fourth gear (36) positioned on a second output shaft (42), a fifth gear (37) positioned on the first branch shaft (40), and a sixth gear positioned on the second branch shaft (41). Gear (38), wherein the gears of the power summation stage (32) are single helical, and wherein the fifth gear (37) and the sixth gear (38) each mesh with the fourth gear (36). Transmission arrangement according to one of Claims 1 , 5 or 6 , characterized in that the amounts of the helix angles running in opposite directions of inclination deviate from one another in such a way that there is a balance of forces on the shafts with regard to the axial forces resulting from the toothing. Drive for a twin-screw extruder, having at least one input shaft to which a motor can be coupled, having a first output shaft (19; 39) to which a first screw shaft of the twin-screw extruder can be coupled, and having a second output shaft (22; 42) to which a second screw shaft of the twin-screw extruder can be coupled, and with a gear arrangement (10; 30) connected between the output shafts (19, 39; 22, 42), characterized in that the gear arrangement (10; 30) according to one of Claims 1 until 7 is trained.

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