Vacuum pump with two co-operating rotors

Abstract

The invention relates to a vacuum pump (1) comprising a pump chamber casing (5) accommodating two co-operating rotors (2, 3) which are respectively arranged on a shaft (8, 9); a bearing/gear chamber (6) adjacent to the pump chamber casing (5) in which the rotor shafts (8, 9) are cantilevered and provided with a synchronisation gear (17); a drive motor (25) whose drive shaft (28) extends parallel to the rotor shafts (8, 9) and is provided with a drive gear (35); also comprising a gear stage (37) between the drive shaft (28) and one of the rotor shafts (8, 9). In order to provide a machine of this type which can be embodied in a compact form, the drive gear (35) of the drive shaft (28) engages directly with a driven gear (36) on one of the rotor shafts (8, 9), forming the gear stage (37).

Description

[0001] The present invention relates to a vacuum pump having the characterising features of patent claim 1.

[0002] Vacuum pumps of this kind belong to the class of two-shaft vacuum pumps. Typical examples of two-shaft vacuum pumps are Roots pumps, claws pumps and screw pumps. The two rotors of such pumps are located in a pump chamber and effect pumping of the gases from an inlet to an outlet. The cantilevered bearing offers, in the instance of axially pumping machines, the benefit that on the suction side (high-vacuum side) shaft seals are not necessary.

[0003] In two-shaft machines with synchronised shafts, direct driving of one of the two shafts is common (c.f. DE 198 20 523 A1, for example). If in machines of this type common AC drive motors are employed, there result rotor speeds of 3000 rpm. (at 50 Hz) and 3600 rpm. (at 60 Hz) respectively. Pumps being operated at such speeds have a low power density, require narrow slots and/or many stages and are for this reason relatively large, heavy and costly. Increasing the speed would be possible with the aid of a frequency converter; however, frequency converters for large drive power ratings are expensive.

[0004] A vacuum pump with the characterising features of patent claim 1 is known from European patent 472 933, drawing FIG. 15. The drive motor is accommodated in a casing at the side next to the pump. In order to be able to operate the rotors at a higher speed compared to that of the motor, a gear is provided. The driving toothed gear of the motor shaft is coupled via a further toothed gear to a toothed gear arranged on one of the rotor shafts. A solution of this kind requires much space. Moreover, four shafts are present which each need to be equipped with bearings.

[0005] It is the task of the present invention to design a vacuum pump of the kind affected here in a more simple and more compact manner.

[0006] This task is solved through the characterising features of the patent claims.

[0007] The essential advantage of the present invention is, that the means which are required for a transmission to the higher speed—doubling of rotor speed, for example—are much simpler compared to the state-of-the-art. Commonly employed motor technology can be retained. In particular when accommodating also the drive motor in the bearing/gear chamber, there result extremely slim and compact designs and in addition cooling of the electric motor is simplified.

[0008] Further advantages and details of the present invention shall be explained with reference to examples of embodiments depicted schematically in drawing FIGS. 1 to 10. Depicted in

[0009] drawing FIGS. 1 to 3 are examples of embodiments according to the present invention, in which the motor rotor runs on a separate motor shaft arranged beside the rotor shafts and

[0010] drawing FIGS. 4 to 10 are examples of embodiments in which the motor rotor and one of the rotor shafts have a joint axis of rotation.

[0011] In the drawing figures, the two-shaft vacuum pump is designated as 1, its rotors as 2, 3, its pump chamber as 4 and is pump chamber casing as 5. Adjoined to pump chamber casing 5 is the bearing/gear chamber 6, the casing of which is designated as 7. The rotor shafts 8, 9 extend into the bearing/gear chamber 7. The axes of rotation of the rotors and the shafts are designated as 11 and 12. The shafts are supported by bearings on the side of the pump chamber and on the side of their ends (bearings 13 to 16) so that the rotors 2, 3 are supported in a cantilevered manner. The rotor shafts 2, 3 are coupled via a synchronising gear 17 being formed by two engaging toothed gears 18, 19. Gaskets 21, 22 are provided for the purpose of sealing off the pump chamber 4 against the bearing chamber 6.

[0012] In all examples of the embodiments depicted, the drive motor 25 is located in the bearing/gear chamber 7. The stator 26 encompasses the armature 27 being affixed on to the motor shaft 28. The motor shaft 28 extends in each instance in parallel to the rotor shafts 8, 9 and is supported by bearings in the area of its ends (bearings 31, 32) in the bearing/gear chamber 7. Its axis of rotation is designated as 29.

[0013] There also exists the possibility of arranging a standard motor outside of casing 7 and to link said motor to a shaft extending within the bearing/gear chamber 6 in parallel to the rotor shafts 8, 9 with the motor shaft carrying the driving toothed gear 35. A solution of this kind is outlined through the dashed line 30 in drawing FIG. 1.

[0014] As an example, a screw vacuum pump 1 is depicted in drawing FIG. 1. Plane 23 (drawing FIGS. 2, 3 and 4) formed by the axes of rotation 11, 12, is perpendicular to the plane of the drawing figure, so that only one rotating unit is visible. During their operation, the rotors 2, 3 pump gases from inlet 33 to an outlet which is not depicted.

[0015] In the screw vacuum pump in accordance with drawing FIG. 1, the motor shaft 28 is adjoined at the side of the plane formed by axes of rotation 11, 12. The motor shaft carries a driving toothed gear (driving gear 35) which directly engages with a toothed gear (driven gear 36). Driving gear 35 and driven gear 36 form a gear stage 37. The driven gear 36 is affixed on to one of the rotor shafts 8, 9. Synchronous driving of the second rotor shaft is in each instance effected through the toothed gears 18, 19 of the synchronising gear 17.

[0016] Drawing FIGS. 2 to 4 outline coupling options of the kind detailed. In the solution according to drawing FIG. 2, the driving gear 35 engages with one (18) of the two synchronising toothed gears 18, 19. The toothed gear 18 acts at the same time as the driven gear 36. The transmission ratio is determined by the ratio between the diameters of the toothed gears 35 and 18.

[0017] The embodiment in accordance with drawing FIG. 3 substantially corresponds to the solution depicted in drawing FIG. 1. Located under the synchronising toothed gear 18 on the shaft 8, there is a further, toothed gear 36 preferably smaller in diameter, which engages with the driving toothed gear 35. The same also applies to the solution in accordance with drawing FIG. 4. The difference compared to drawing FIG. 3 is that the axes of rotation 11, 12 and 29 are located in one plane.

[0018] From drawing FIGS. 2 to 4 it is apparent that on the one hand the usable space between the rotor shafts 8, 9 may be utilised in part for the motor stator 26 (drawing FIGS. 2, 3) so that compact solutions will result. On the other hand the angle between the respective axes of rotation may be selected almost free of any restrictions.

[0019] In the embodiments in accordance with drawing FIGS. 5 to 10, the motor shaft 28 is designed to be hollow, so that there then exists the possibility of letting one of the rotor shafts penetrate the hollow shaft 28 in such a manner that the axes of rotation 29 and 11 respectively 12 are identical. In embodiments of this kind the usable space between the rotor shafts 8, 9 may be utilised even better. In all, there results from this an optimally compact and slim shape.

[0020] Some of the design options for such embodiments are depicted in drawing FIGS. 5 to 10. In the solutions in accordance with the drawing FIGS. 5 and 6, the hollow shaft 28 carries in each instance the driving gear 35 which engages with the driven gear 36 on the rotor shaft located besides the hollow shaft 28. The synchronisation gears1) 17 offset which respect to this is employed for synchronised driving the rotor shaft 8 penetrating the hollow shaft 28. Also in the drawing FIGS. 7 and 8 a driving gear 35 and a driven gear 36 form the gear stage 37. Outlined in drawing FIG. 7 is, that the gear stage is designed by way of chain or belt2) stages. The solution in accordance with drawing FIG. 8 is equipped with a planet gear. 1) Translator's note: The German text states “Synchronisationsbetriebe” here whereas “Synchronisationsbetriebe” would be correct. Therefore the latter has been assumed for the translation. 2) Translator's note: The German text states “Riemenstufen” here whereas “Riemenstufen” would be correct and in line with the text of claim 12. Therefore the latter has been assumed for the translation.

[0021] The bearing arrangement for motor shaft 28 may be effected independently of the bearings 13 to 16 for rotor shafts 8, 9 by means of carriers affixed to the casing (drawing FIG. 8, upper bearing 31). An especially compact solution is attained when the motor shaft 28 is supported by at least one (drawing FIG. 8, bearing 32) preferably both bearings 31, 32 (drawing FIGS. 5 and 7) on the rotor shaft 8 penetrating the hollow shaft 28. Moreover, the rotor shaft 8 penetrating the hollow shaft 28 may be supported within the hollow shaft (bearings 15 in drawing FIG. 6). Finally there is depicted in drawing FIG. 7 as a special feature that the transmission ratio of the synchronising stage may differ from 1:1. The toothed gears 18 and 19 have differing diameters, outlining a transmission ratio of 2:1. Required for this is that the rotors 2, 3 be designed correspondingly.

[0022] Drawing FIGS. 8 to 10 depict the way in which the hollow motor shaft 28 is coupled to the rotor shaft 8 centrally penetrating the hollow shaft, said coupling being effected by a planet gear 41, forming the gear stage 37. The planet gear comprises in a manner which is basically known the outer ring gear 42, for example two planet gears 43, 44 as well as the sun gear 45 affixed to the rotor shaft 8 with axis of rotation 29. Schematic diagram 9 depicts the solution presented in drawing FIG. 8 with a fixed ring gear 42. The plant gears 43, 44 which are joined via cranks 46, 47 to the motor shaft 28, form the driving gears 35, 35′. Only one planet gear 44 would suffice as the driving gear 35 (drawing FIG. 9). The sun gear 45 forms the driven gear 36.

[0023] In the solution in accordance with drawing FIG. 10 the ring gear 42 forms the driving gear 35. For the planet gear 443) a fixed carrier is provided. The sun gear 45 again forms the driven gear 36. Although in the instance of this solution the driving gear 35 and the driven gear 36 no not engage directly, the aims of the invention—compact, simple—can be attained. 3) Translator's note: The German text states “4” here whereas “44” would be correct and in line with the drawing figures. Therefore the latter has been assumed for the translation.

[0024] It has already been proposed to equip at least one of the rotor shafts 8, 9 with a central bore and to utilise said bore(s) for conveying a lubricating and cooling agent (preferably oil). Where the drive motor 25 is arranged within the bearing/gear chamber, said motor may also be cooled with the oil. An oil pump for pumping the oil may be arranged on one of the shafts 8, 9 or 28. If the motor shaft 28 should be located besides the rotor shafts 8, 9 then a particularly expedient solution is such that the oil pump—preferably designed as an eccentric pump—be arranged on the motor shaft 28, specifically in the area of its upper end. This embodiment is depicted in drawing FIG. 1. The oil pump is designated as 51. In addition, one of the shafts 8, 9 or 28 may be run out, on its side adjacent to the pump chamber, from the bearing/gear chamber 6 in a sealed manner and carry a ventilating wheel 52. Expediently, to this end also the motor shaft 28 is utilised in accordance with drawing FIG. 1.

Claims

1. Vacuum pump (1) comprising a pump chamber casing (5) accommodating two co-operating rotors (2, 3) which are respectively arranged on a shaft (8, 9); a bearing/gear chamber (6) adjacent to the pump chamber casing (5), in which the rotor shafts (8, 9) are cantilevered and provided with a synchronisation gear (17); a drive motor (25) whose drive shaft (28) extends parallel to the rotor shafts (8, 9) and is provided with a drive gear (35); also comprising a gear stage (37) between the drive shaft (28) and one of the rotor shafts (8, 9), wherein the drive gear (35) of the drive shaft (28) engages directly with a driven gear (36) on one of the rotor shafts (8, 9), forming the gear stage (37).

2. Pump according to claim 1, wherein the drive gear (35) of the drive shaft (28) engages with one of the toothed gears (18, 19) of the synchronisation gear (17) having, compared to the driving gear (35), a smaller diameter.

3. Pump according to claim 1, wherein the drive gear (35) of the drive shaft (28) engages with a toothed gear (36) on one of the rotor shafts (8, 9), said toothed gear having, compared to the synchronising toothed gear (18 and 19 respectively) on this shaft, a smaller diameter.

4. Pump according to one of the above claims, wherein the drive motor (25) is accommodated within the bearing/gear chamber (6).

5. Pump according to claim 4, wherein the motor shaft (28) is located beside the rotor shafts (8, 9).

6. Pump according to claim 5, wherein at one end of the motor shaft (28), preferably at it's end on the pump chamber side, there is located an oil pump (51).

7. Pump according to claim 5 or 6, wherein the motor shaft (28) is run, at its end adjacent to the pump chamber, out of the gear/bearing chamber (6) and carries a ventilating wheel (52).

8. Pump according to claim 4, wherein the drive shaft (28) of the drive motor (25) is of hollow design and where one of the rotor shafts (8, 9) penetrates the hollow drive shaft (28).

9. Pump according to claim 8, wherein the rotor shaft (8 and 9 respectively) penetrating the hollow shaft (28) is supported by the casing (7) via bearings (13, 15) and where at least one of the two bearings (31, 32) of the motor shaft (28) is supported on the rotor shaft (8 and 9 respectively).

10. Pump according to claim 8, wherein the rotor shaft (8 and 9 respectively) penetrating the hollow shaft (28) is supported by at least one bearing (31 and 32 respectively) in the hollow shaft (28).

11. Pump according to one of the claims 8, 9 or 10, wherein as the gear stage (37) there is provided a planet gear (41) with a fixed ring gear (42).

12. Pump according to one of the claims 1 to 10, wherein a chain or belt stage forms the gear stage (37).

13. Vacuum pump (1) comprising a pump chamber casing (5) accommodating two co-operating rotors (2, 3) which are respectively arranged on a shaft (8, 9); a bearing/gear chamber (6) adjacent to the pump chamber casing (5), wherein the rotor shafts (8, 9) are cantilevered and provided with a synchronisation gear (17); a drive motor (25) whose drive shaft (28) extends parallel to the rotor shafts (8, 9) and is provided with a drive gear (35); also comprising a gear stage (37) between the drive shaft (28) and one of the rotor shafts (8, 9), wherein the drive shaft (28) of the drive motor (25) is of hollow design, where one of the rotor shafts (8, 9) penetrates the hollow drive shaft (28) and where as the gear stage (37) a planet gear (41) with driven ring gear (42) and a fixed sun wheel is provided.

14. Pump according to one of the above claims, wherein the synchronising gear (17) has a transmission ratio differing from 1:1.

15. Pump according to one of the above claims, wherein the toothed gears employed in the pump are made of plastic for the purpose of reducing noise.