U.S. patent application number 10/169329 was filed with the patent office on 2005-03-31 for cooled screw vacuum pump.
Invention is credited to Kriehn, Hartmut.
Application Number | 20050069446 10/169329 |
Document ID | / |
Family ID | 7934616 |
Filed Date | 2005-03-31 |
United States Patent
Application |
20050069446 |
Kind Code |
A1 |
Kriehn, Hartmut |
March 31, 2005 |
Cooled screw vacuum pump
Abstract
The invention relates to a screw vacuum pump, comprising two
shafts (7, 8), each bearing a rotor (3, 4) containing a hollow
chamber (31). Said chamber (31) contains a second hollow chamber
(32) which embodies a component of a coolant circuit. The shafts
(7, 8) have open bores (41) on the delivery side, through which the
coolant is supplied and evacuated to or from the additional hollow
chambers (32). In order to improve the effectivity of the cooling
of the rotors, guide components (44) are located in the open bores
(41) of the shafts (7, 8). Said guide components separately guide
the inflowing and outflowing coolant.
Inventors: |
Kriehn, Hartmut; (Koln,
DE) |
Correspondence
Address: |
Fay Sharpe Fagan
Minnich & McKee
Seventh Floor
1100 Superior Avenue
Cleveland
OH
44114-2518
US
|
Family ID: |
7934616 |
Appl. No.: |
10/169329 |
Filed: |
October 1, 2002 |
PCT Filed: |
December 7, 2000 |
PCT NO: |
PCT/EP00/12318 |
Current U.S.
Class: |
418/83 ;
418/201.1; 418/94 |
Current CPC
Class: |
F04C 29/04 20130101;
F04C 18/16 20130101 |
Class at
Publication: |
418/083 ;
418/094; 418/201.1 |
International
Class: |
F01C 021/04; F04C
015/00 |
Foreign Application Data
Date |
Code |
Application Number |
Dec 27, 1999 |
DE |
19963171.9 |
Claims
1. A screw vacuum pump, comprising: two shafts, each bearing a
rotor containing a first hollow chamber; said first chambers each
containing a second hollow chamber which defines a coolant channel;
the shafts have open bores on a delivery side, through which
inflowing coolant is supplied to and outflowing coolant is
evacuated from the second hollow chambers; guide components located
in the open bores of the shafts, said guide components separately
guiding the inflowing and outflowing coolant.
2. The pump according to claim 1, wherein the open bores include:
lateral sections of longitudinal grooves or outer sections turned
off on a lathe in the guide components.
3. The pump according to claim 1, wherein the guide components
include: axial and radial line sections arranged to allow for
separate crossing guidance of the inflowing coolant and the
outflowing coolant.
4. The pump according to claim 3, further including: a first
longitudinal groove or a pair of longitudinal grooves for supplying
the inflowing coolant; and a second longitudinal groove or pair of
longitudinal grooves offset by 90 degrees for evacuating the
outflowing coolant.
5. The pump according to claim 4, further including: cross bores
which cross the inflowing and outflowing coolant flows.
6. The pump according to claim 1, further including: radial bores
linking the open bores to the second hollow chamber.
7. The pump according to claim 1, wherein the guide components
comprise: three sections which divide the open bore in each shaft
into three partial chambers which are each located at a level of a
radial cross bore, longitudinal bores in the three sections and
line sections linking said longitudinal bores, separate inflowing
and outflowing coolant.
8. The pump according to claim 1, further including: lines for
evacuating the coolant out into a gear chamber.
9. The pump according to claim 1, wherein an end of each shaft on
the suction side is linked to an end of the rotor on the delivery
sides and the guide component extend up to and into the first
hollow chambers.
10. The pump according to claim 9, wherein the guide components are
made of a light plastic material.
11. The pump according to claim 1, wherein the first hollow
chambers fully penetrates the rotors and the guide components
function as tie rods for affixing the rotors to the shafts.
12. The pump according to claim 1, wherein an inside wall of each
first hollow chamber limits the second hollow chamber and widens
conically in a direction of the delivery side.
13. The pump according to claim 1, wherein each second hollow
chamber is a relatively narrow cylindrical section of an annular
ring through which the coolant flows, the section of the annular
ring extending between one of the shaft and the guide component and
a corresponding inner wall of the first hollow chamber and between
a suction side and the delivery side of the rotor.
14. The pump according to claim 13, wherein: the shaft is connected
on the delivery side with the rotor and the guide component extends
into the first hollow chamber in the rotor and the guide component
and the inner wall of the rotor form the annular ring.
15. The pump according to claim 13, wherein the annular ring is
located directly between the shaft and the inner wall of the first
hollow chamber.
16. The pump according to claim 13, wherein the shaft is equipped
with a sleeve, the outside of which limits the annular ring.
17. The pump according to claim 1, wherein the rotor has delivery
side and suction side sections and delivery side and suction side
hollow chambers are defined through which the coolant flows, said
delivery side and suction side chambers being supplied through
channels in the guide component.
18. The pump according to claim 17, wherein: the shaft penetrates
the rotor at the delivery side section; the suction side section is
connected to an end of the shaft on the delivery side; the guide
component extends up to and into the suction side hollow chamber of
the suction side rotor section and limits the suction side hollow
chamber.
19. The pump according to claim 1, wherein a direction of the
flowing coolant is so selected that the flow passes through the
second hollow chamber from the delivery side in the direction of a
suction side.
20. The pump according to claim 1, further including: coolant pumps
located in an area of the shaft ends on the delivery side.
Description
[0001] The present invention relates to a screw vacuum pump,
comprising two shafts, each bearing a rotor containing a hollow
chamber. Said chamber contains a second hollow chamber which
embodies a component of a coolant circuit. The shafts have open
bores on the delivery side, through which the coolant is supplied
and evacuated to or from the additional hollow chambers.
[0002] A screw vacuum pump having these features is known from
DE-A-198 20 523 (drawing FIG. 4). The coolant is injected into the
bores in the shafts, said bores being open on the delivery side. On
the suction side, the shafts are equipped with radial bores,
through which the coolant enters into the hollow chambers in the
rotor. The outside walls of these hollow chambers are designed to
be conical, widening in the direction of the delivery side. Thus
the coolant film forming on the outside walls flows in the
direction of the delivery side. Via radial bores in the shaft on
the delivery side the hot coolant returns through the respective
central bore in the shaft and flows through these bores back to the
respective opening. Of disadvantage in the instance of the known
solution is, that the cold coolant is supplied and the hot coolant
is evacuated in each case through a common bore in the shafts.
Mixing of the coolant flows is unavoidable whereby the effectivity
of the cooling arrangement is already impaired. Moreover, it is not
possible to operate the cooling facility for the rotors in a
"counterflow". The coolant first arrives at the cooler side of the
rotors (on the suction side) and thereafter it flows to the
delivery side where the amount of heat of compression which needs
to be dissipated is greatest. Finally, the solution according to
the state-of-the-art requires that the corresponding rotor chambers
be designed to be conical, which can only be implemented with a
manufacturing-wise relatively high complexity.
[0003] It is the task of the present invention to not only improve
the supply of coolant into the rotor chambers in the instance of a
screw vacuum pump of the kind mentioned above, but also improve the
effectivity of the cooling arrangement.
[0004] This task is solved through the characterising features of
the patent claims.
[0005] By employing guide components inserted in the central shaft
bores, initially a reliable and effective separation between the
inflowing cold coolant and the outflowing hot coolant can be
attained, in particular when the guide components are manufactured
of a material which does not conductheat very well. The central
shaft bore for accommodating the guide component may have a
relatively large diameter. Such a bore can be manufactured in the
shaft material in a significantly easier manner compared to
individual deep bore holes for the supply and evacuation channels.
Moreover, guide components will allow cooling of the rotors in a
"counterflow", since even trouble-free crossing of the supplied and
evacuated coolant flows can be arranged. Cooling the rotors in a
counterflow offers the additional advantage of a more even
temperature distribution, so that the slots between rotor and
casing can be maintained small and uniform. Finally, the guide
components allow cooling of the rotors in such a manner that all
lines, slots, chambers or alike which are located within the rotor
chambers and through which the coolant flows, are filled at all
times completely with the flowing coolant. The effectivity of the
cooling arrangement is thus considerably improved.
[0006] Further advantages and details of the present invention
shall be explained with reference to the design examples depicted
schematically in drawing FIGS. 1 to 7. Depicted is/are in
[0007] drawing FIG. 1 a sectional view through a screw vacuum pump
according to the present invention,
[0008] drawing FIGS. 2 and 3 sectional views through one each of
two cantilevered rotors of a screw vacuum pump, depicting further
solutions for the design of the guide component,
[0009] drawing FIG. 4 a sectional view through a rotor with means
of displacing the cooling slot to the outside,
[0010] drawing FIGS. 5 and 6 a solution in which the guide
component limits the cooling slot, and
[0011] drawing FIG. 7 a solution with a rotor consisting of two
sections.
[0012] The screw vacuum pump 1 depicted in drawing FIG. 1 comprises
pump chamber casing 2 with the rotors 3 and 4. Inlet 5 and outlet 6
of the pump 1 are schematically marked by arrows. The rotors 3 and
4 are affixed on to the shafts 7 and 8 respectively, said shafts
being each supported by two bearings 11, 12 and 13, 14
respectively. One bearing pair 11, 13 is located in a bearing plate
15 which separates the pump chamber being free of lubricant from a
gear chamber 16. The second bearing pair 12, 14 is located within
pump chamber casing 2. Located in casing 17 of the gear chamber 16
are the synchronising toothed wheels 18, 19 affixed to the shafts 7
and 8, as well as a pair of toothed wheels 21, 22 serving the
purpose of driving the pump 1, where one toothed wheel is coupled
to the shaft of the drive motor 23 arranged vertically besides the
pump 1. Moreover, the gear chamber has the function of an oil sump
20.
[0013] The ends of the shafts 7, 8 on the side of the gear chamber
penetrate through bores 24, 25 in the bottom of the gear chamber
casing 17 and end in an oil containing chamber 26 being formed by
casing 17 and a thereto affixed trough 27. In the design example
depicted, in which the pair of rotors 3, 4 is supported by bearings
on both sides, the oil sump 16 is separated from the oil containing
chamber 26 by seals 28, 29. In the instance of a cantilevered
bearing for the pair of rotors 3, 4 the second pair of bearings 12,
14 is located in the area of the bores 24, 25.
[0014] From drawing FIG. 1 it is apparent that the rotors 3 and 4
each have a hollow chamber 31 in which the shaft 8 extends and in
which a further chamber 32 is present through which coolant flows.
Since only rotor 4 is depicted by way of a partial section, the
present invention is explained only with reference to this rotor
4.
[0015] In the solution according to drawing FIG. 1, the chamber 32
through which the coolant flows is designed by way of a section of
an annular gap and is located directly between shaft 8 (resp. 7)
and rotor 4 (resp. 3). To this end the cylindrical inner wall of
the rotor containing the hollow chamber 31 is equipped in its
middle area with a section 33 turned off on a lathe, the depth of
which corresponds to the thickness of the cooling slot 32. On the
suction side and the delivery side, the shaft 8 rests flush against
the inner wall of the hollow chamber 31.
[0016] The cooling slot 32 is supplied with the coolant through the
shaft 8. It is equipped with a central bore 41 extending from the
bottom end of the shaft 8 to the end of the cooling slot 32 on the
delivery side. It forms a chamber 43 in which a guide component 44
for the coolant is located. The guide component 44 extends from the
bottom end of the shaft 8 up to and over the end of the cooling
slot 32 on the delivery side. The coolant is supplied via the
longitudinal bore 45 in the guide component 44, said bore being
linked via truly aligned cross bores 46 through the component 44
and the shaft 8 to the end of the cooling slot 32 on the delivery
side.
[0017] At the level of the cooling slot 32 on the suction side, the
shaft 8 is equipped with one or several cross bores 47 which open
out into the chamber 43 formed by the pocket hole 41 and the face
side of the guide component 44. Said chamber is linked via the
longitudinal bore 48 and the truly aligned cross bores 49 (in the
guide component 44 and in the shaft 8) to the gear chamber 16.
[0018] The coolant is supplied from the oil containing chamber 26
through bores 45 and 46 into the cooling slot 32. The coolant flows
through the cooling slot 32 from the delivery side to the suction
side of the rotor 4. Since most of the heat which needs to be
dissipated is generated on the delivery side of the rotor 4, the
rotor 4 is cooled in a counterflow. The coolant is evacuated
initially through the second bore 47 in the chamber 43 in the shaft
8 as well as through the bores 48, 49. The bore 48 extends from the
suction side of the cooling slot 32 up to the level of the gear
chamber 16. The cross bore 48 provides the link between bore 43 and
the gear chamber 16.
[0019] Reliable cooling of the rotors 3, 4 is attained when the
coolant is capable of flowing through the relatively narrow cooling
slots 32 quickly and undisturbed (free of cavitation and
contamination). For this reason it is expedient to ensure, besides
cooling and filtering of the coolant, a sufficient pumping force.
In the design example in accordance with drawing FIG. 1, therefore,
the gear chamber 16, resp. the oil sump 20 is linked to the chamber
26 through a line 51 in which there is located besides a cooler 52
and a filter 53, an oil pump 54 which may be designed by way of a
gear pump, for example. The oil pump 54 ensures that the coolant
enters at the necessary pressure and free of cavitation from
chamber 26 into the bore 41.
[0020] Moreover, there exists the possibility of arranging oil
pumps (centrifugal pumps, gear pumps) in the area of the bottom
ends of the shafts 7, 8. However, these need to be so designed that
they are capable of meeting the requirements as to the desired
pumping properties.
[0021] Depicted in drawing FIG. 2 is a solution in which the guide
component 44 comprises three sections 61, 62, 63 which divide the
hollow chamber in the shaft 8 in to three partial chambers 64, 65,
43 which are each located at the level of the cross bores 49, 46
and 47. Through suitable bores in the sections 61 to 63 as well as
line sections 67 and 68 linking said bores, separate supply and
evacuation of the coolant may be implemented.
[0022] In the embodiment in accordance with drawing FIG. 3, the
coolant is supplied through the bore 45, which in contrast to the
embodiments in accordance with drawing FIGS. 1 and 2 centrally
penetrates the guide component 44. The oil pumped by a centrifugal
pump 71 into the bore 45 enters into the hollow space 43 formed by
the pocket hole 41 as well as the guide component 44, and through
the cross bore 46 into the chamber 32 through which the coolant
flows. In contrast to the embodiments in accordance with drawing
FIGS. 1 and 2, the chamber 32 through which the coolant flows has
the shape of an annular chamber of a relatively large volume being
formed by the shaft 8 and the inner wall of the hollow chamber 31.
Since this inner wall is designed to be conical in such a manner
that the rotor's hollow chamber 31 widens conically in the
direction of the delivery side of the rotors 3, 4, the coolant
injected from the bores 46 into the chamber 32 is conveyed in the
direction of the rotor's delivery side. Bubble- or cavitation-free
operation of the coolant circuit is not required. The coolant can
be so metered that it will flow along the inner wall of the rotor's
hollow chamber 31 by way of a thin film, for example.
[0023] The evacuation bores 47 are linked to lateral side channels
72 (or a section turned off on a lathe) in guide component 44
whereby said evacuation bores extend at the level of the bearing
plate 15 up to the gear chamber 16 where they are linked to the
cross bores 49.
[0024] The embodiment in accordance with drawing 4 differs from the
embodiments detailed above in that a bore is provided fully
penetrating the shaft 8 and the rotor 4. For the formation of the
hollow chamber 31, a cover 76 is provided on the suction side, this
cover being linked via a bolt 77 with the guide component 44. The
guide component 44 is firmly inserted from the suction side.
Together with bolt 77 and the cover 76 it serves the purposes of
axially affixing the rotor 4. On the delivery side, bore 41 has a
smaller diameter.
[0025] The shaft 8 is equipped with an outer sleeve 77 which
together with the inner wall of the hollow chamber 31 in the rotor
4 forms the cooling slot 32.sup.1). This slot extends substantially
only at the level of the delivery side of the rotor 4. Radially
displacing the cooling slot 32 towards the outside improves the
cooling effect. The coolant is only supplied through relatively
short sections of longitudinal grooves 78 (or a section turned off
on a lathe, annular channel) in the guide component 44 up to the
cross bores 46 which penetrate the shaft 8 and the sleeve 77.
Before it enters into the longitudinal grooves 78, it flows through
bores 79, 80 in the bearing plate 15 as well as the chamber 82 on
the bearing side of an axial face seal 83 where it ensures the
formation of the necessary barrier pressure. The coolant is
returned through the cross bores 47 as well as the central bore 45
in the guide component 44, resp. the bore 41 in the shaft 8.
.sup.1)Translator's note: In the figure "34" is stated "32" would
be more in line with the remaining text and the other drawing
figures.
[0026] In the solution in accordance with drawing FIGS. 5a and
5b.sup.2), the shaft 8 does not extend into the rotor's hollow
chamber 31. Said shaft is linked to the rotor 4 at the level of the
delivery side. The guide component 44 in the rotor's hollow space
31 has a section 84 with an increased diameter which together with
the inner wall of the hollow chamber 31 in rotor 4 forms the
cooling slot 32. A second section 85 having, compared to the
section 84 a smaller diameter, penetrates the bore 41 in the shaft
8.
[0027] For thermal reasons of permitting on the one hand the supply
of the coolant from the open side of the bore 41 through a central
bore 45 in the guide component 44 and on the other hand to permit
cooling of the rotor 4 in a counterflow, it is required that the
guide component 44 provides a crossing for the coolant flows. This
is implemented through cross bores and outer groove sections in the
guide component 44 which are designed as detailed in the following
(cf. drawing FIGS. 5a, 5b and 6):
[0028] Coolant supplied.sup.3) centrally through the pocket hole 45
enters through a cross bore 88 into two groove sections 89 facing
each other and then the coolant enters into the hollow chamber 31
(delivery side). Thereafter the coolant flows through the cooling
slot 32 and enters through cross bores 47 into a line section 89
located centrally in the guide component. Said line section extends
to a second cross bore 90 placed on the suction side with respect
to the first cross bore 88. The two cross bores 88 and 90 are
arranged approximately perpendicular to each other. The cross bore
90 .sup.2)Translator's note: The German text states " . . . nach
den FIG. 5a erstreckt . . . " here whereas " . . . nach den FIG. 5a
und 5b erstreckt . . . " would make for a correct sentence.
Therefore the latter has been assumed for the translation.
[0029] opens out into groove sections 91 facing each other, which
are offset by about 90 degrees with respect to groove sections 89.
Thus it is possible.sup.4) to guide the returning coolant through
these groove sections 91 to the cross bores 49 in the area of the
gear chamber 16.
[0030] In the design example in accordance with drawing FIG. 7, the
rotor 4 comprises two sections 4' and 4" having differently
designed threads as well as each with a hollow chamber 31' and 31"
respectively. The shaft 8 extends into the hollow chamber 31" of
the rotor section on the delivery side 4" and thus forms the
cooling slot 32". The guide component 44 is similarly designed as
in the embodiment in accordance with drawing FIGS. 5, 6. It has a
section 84 with an increased diameter which is located in hollow
chamber 31' of the rotor section 4' and which forms together with
the inside wall of this rotor section 4' the cooling slot 32'. A
further section 85 of the guide component 44 having a smaller
diameter penetrates the central bore 41 in shaft 8. The guide
component 44 is equipped with a central bore 45 extending to the
suction side of the rotor 4.
[0031] For simplicity and better overview, a solution is presented
in which the coolant is supplied through the central bore 45 and
where the coolant flows through lateral bores 46' in section 84 on
the suction side into the cooling slot 32'. Through a section 78'
turned off on a lathe (or also through longitudinal grooves) as
well as cross bores 46" the end of the cooling slot 32" on the
delivery side is linked to the end of the .sup.3)Translator's note:
The German text states " . . . zugefhrtes Khlmittel wird ber eine
Querbohrung . . . " here whereas " . . . zugefhrtes Kuhlmittel
gelangt ber eine Querbohrung . . . " would make for a complete
sentence. Therefore the latter has been assumed for the
translation. .sup.4)Translator's note: The German text states " . .
. moglich dass das . . . " here whereas " . . . moglich das . . . "
would make for a complete sentence. Therefore the latter has been
assumed for the translation.
[0032] cooling slot 32" on the suction side so that the coolant
passes sequentially through the two cooling slots 32', 32". Through
a further section 78" turned off on a lathe, the evacuation opening
47" on the delivery side of the cooling slot 32" is linked to the
evacuation opening 49 at the level of the gear chamber 16. Also in
the instance of this solution there exists the possibility of also
employing the guide component 44 as a tie rod, specifically for
affixing the rotor section 4'.
[0033] Of course there also exists the possibility in the instance
of the embodiment in accordance with drawing FIG. 75) of designing
the supply and evacuation lines for the coolant in such a manner
that the cooling slots 32', 32" are supplied separately and/or in a
counterflow.
[0034] The solutions in accordance with drawing FIGS. 5 to 7 are of
particular advantage when the rotors 3, 4 are cantilevered, since
then there exists the possibility of .sup.5)Translator's note: The
German text states "FIG. 9" whereas "FIG. 7" would be appropriate.
Therefore the latter has been assumed for the translation.
[0035] manufacturing the guide component 44.sup.6) of light
materials like plastic, for example. Thus the mass of the rotors
far from the bearing can be kept small. The usage of plastic or
similar materials also offers the general advantage that there are
located between the inflowing and the outflowing coolant materials
which do not conduct heat very well. .sup.6)Translator's note: The
German text states "62" here whereas "44" would be more in line
with the remaining text and the other drawing figures. Therefore
"44" has been assumed for the translation.
* * * * *