WO2008003657A1 - Antrieb für eine schraubenspindelpumpe - Google Patents
Antrieb für eine schraubenspindelpumpe Download PDFInfo
- Publication number
- WO2008003657A1 WO2008003657A1 PCT/EP2007/056585 EP2007056585W WO2008003657A1 WO 2008003657 A1 WO2008003657 A1 WO 2008003657A1 EP 2007056585 W EP2007056585 W EP 2007056585W WO 2008003657 A1 WO2008003657 A1 WO 2008003657A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- drive
- crown
- oil
- screw
- pump
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/007—General arrangements of parts; Frames and supporting elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/0085—Prime movers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/025—Lubrication; Lubricant separation using a lubricant pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
- F01C17/02—Arrangements for drive of co-operating members, e.g. for rotary piston and casing of toothed-gearing type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/809—Lubricant sump
Definitions
- Drying pumps are becoming increasingly important, especially in vacuum technology, because increasing obligations in environmental protection regulations and rising operating and disposal costs and increased demands on the purity of the pumped medium, the known wet-running vacuum systems, such as liquid ring machines and rotary vane pumps are increasingly replaced by dry-compressing pumps.
- These dry compacting machines include screw pumps, claw pumps, diaphragm pumps, piston pumps, scroll machines and Roots pumps.
- these machines have in common that they still do not meet today's demands in terms of reliability and robustness and size and weight with low price level.
- the dry compressing screw pump should be operated with air cooling, because a water cooling customer usually requires too much effort.
- the guidance of the cooling air is difficult because additional components must be flowed around with the clutch and motor, whereby the flow resistance increases, so that the fan is complex.
- the aim in the structural design must therefore be that the cooling air flow in the drive area can flow as freely as possible with low resistances.
- the object of the present invention is to maintain for a dry-compressing screw pump with a crown / bevel gear drive when using standard / standard electric motors both the dimensions (especially in the width) of "wet" runners through the usual elongated design and to make the exit of the cooling air as simple and low-resistance.
- this object is achieved in that a standard / standard motor is set transversely to the screw spindle rotor pair and parallel to the crown / bevel gear shaft and via a belt drive with customizable translation ebendiese crown / bevel gear shaft drives for further power transmission to the screw rotor pair via the crown / bevel gear teeth with a simultaneously mounted on this crown / bevel gear drive shaft impeller, preferably on the belt side of the crown / bevel gear shaft.
- the design is preferably chosen as a foot motor, either for the so-called "wall mounting" on the crown / bevel gearbox housing or as a floor mounting on the pump base plate.
- the connection of these respective standard / standard motors is particularly simple in this embodiment according to the invention, because neither a flange nor a coupling must be adapted. It is only to put the pulley directly on the engine shaft end and make the engine-foot assembly, which is much more convenient than the previous procedure.
- the transverse drive motor with belt drive ratio another advantage in terms of easy speed adjustment. Because in a dry-compressing screw pump is because of the non-contact operation of the two screw rotors in the pump room, the performance of the entire pump by speed variation very directly adapted to the application-specific requirements low.
- This objective is particularly simple and advantageous to implement in the present invention, because at constant ratio in the crown / bevel gear stage now just the ratio of the belt stage must be varied. For a constant translation in crown / bevel gear drive is low, because thus an intervention in the interior of the pump can be avoided. Because the outside of the belt is very good and easy to access and the speed adjustment by simply changing the pulleys is extremely convenient and easy to use.
- the crown / bevel gear stage can be optimally executed with regard to the gear parameters as well as the interface adaptation and execution of the tools. Because it is known that for a speed adjustment of the change in the crown / bevel gear drive stage significantly more complex than the simple belt change.
- the power adaptation in the modular system of a screw-spindle pump series is an essential objective for the approximation of the pump performance data, such as, for example, the pumping speed characteristic curve, final pressure, temperature level and power requirement.
- the speed of the screw spindle rotor pair must be adjusted. As usual speed variation widths about ⁇ 50% are desired, which is due to the belt Translation is covered comfortably and safely.
- auxiliary units are now required for operating the screw pump.
- This is firstly a cooling fan, because such screw pumps are usually operated air-cooled, and secondly an oil pump, because such a screw pump according to the document WO 00/12899 preferably with a rotor inner Cooling be provided, for which the coolant, preferably oil, is to be promoted in the rotor bores.
- oil pump are commercially available oil feed pumps, such as internal gear pump.
- these two auxiliary units are set directly to each shaft end of the crown / bevel gear drive shaft, preferably the cooling fan to the shaft end with the drive pulley and the oil pump to the other end of the shaft because of the particularly favorable accessibility for adjustment / assembly work as well as incoming and outgoing lines.
- the drive shaft has a constant speed, usually the direct standard / standard motor speed and the desired speed increase for the screw spindle rotor pair is achieved by changing the crown / bevel gear drive gears.
- the rotational speed of the screw spindle rotors increases in general, the power requirement of the entire machine and the two aforementioned auxiliary units cooling fan and oil pump must bring a higher performance. Up to now, this has been achieved either by overdimensioning or changing the cooling fan or oil pump.
- the upstream belt drive dampens the known starting torque.
- shock of the standard / standard motor and also in operation there are compared to the directly coupled motors, for example via a known dog clutch, with the belt drive a significant vibration damping.
- the standard / standard motor can additionally be attached to its feet via vibration buffers or via a known motor plate with elastically resilient damping elements.
- Fig. 1 shows an exemplary embodiment of the present invention with a section through the entire screw pump.
- the counter-rotating screw spindle rotor pair (1) rotates in a pump housing (2) with a gas inlet (3) and a gas outlet (4).
- This screw spindle rotor pair (1) is driven by a crown / bevel gear drive (5) on the crown / bevel gear drive shaft (6) with the standard / standard motor (7) lying parallel to this drive shaft (6) via a belt drive (FIG. 8th).
- the drive shaft (6) which is completely mounted in the gear housing (9), has, in addition to the pump-side pulley (10), the cooling fan (11), which is exemplified here as an axial fan, and at the other end of the shaft as a further auxiliary unit an oil pump (12), which is exemplified here as êtffyradölpumpe.
- the necessary setting of the correct belt tension for the drive belt (8) takes place here by way of example by means of spacer-underlay elements (13) under the foot mounts of the standard / standard motor (7), which is here mounted, for example, directly on the gearbox housing (9). Of course, a flat mounting on a base plate together with the screw pump is possible.
- the drive belt (8) is provided as usual with a cover (14).
- the oil pump (12) conveys the cooling oil into the conical rotor bore (16) for cooling the screw spindle rotors (1).
- the so-called "operating page” lies on the side of the gear cover (21) with oil sight glass and oil filler and oil drain plug, which are not shown separately here as Simpel elements.
- Fig. 2 shows an example of a side view of the present invention with a partial sectional view.
- the ribbed pump housing (2) with a partially shown screw spindle rotor (1) is fixedly mounted on the crown / bevel gear housing (9). Because of the necessary deflection of the cooling air flow, this transmission housing (9) is designed to be favorable in terms of flow, in that the transitions for the air flow are uniform and gentle.
- the standard / standard motor (7) transmits its power with its motor-side pulley (18) via the drive belt (8) to the pump-side pulley (10) on the crown / bevel gear drive shaft (6) according to the diameter Ratio of the two pulleys at the desired speed to the screw pump.
- the required belt tension with simultaneous vibration and inrush damping is generated in this illustration by way of example via a motor plate (17) with a rotary joint (20) and a spring-damping element (19).
- Fig. 3 shows how Fig. 1 shows an exemplary embodiment of the present invention with a section through the entire screw pump.
- the oil pump (12) receives frothy oil when sucking in, as occurs, for example, in the transmission oil chamber (29) by the crown or bevel gear drive and by the escaping oil from the spindle rotors. So that the oil pump (12) can aspirate as calm as possible oil, the direct connection from the transmission oil chamber (29) to the suction oil chamber (30) by a continuous partition (23) is avoided, preferably the support bearing (22) for the drive shaft (6) is placed in this partition wall (23). As shown in Fig. 5 additionally shown, the oil now flows from the transmission oil chamber (29) via the large calming and supply oil space (31) to the intake oil chamber (30). All three oil rooms, so
- Calming and storage oil space (31) are directly connected to each other via oil passage openings (25) and have the same oil level at standstill.
- the drive motor (7) is mounted on the enlarged gear housing (9).
- Fig. 4 shows how Fig. 2 by way of example a side view.
- the gear housing (9) according to FIG. 4 is designed so that the drive motor (7) extends to the gear housing part (9) extending under this motor (7). is set. With the modern belt drives the complex adjustment of the belt tension, as shown in Fig. 2, conveniently no longer required.
- the pump facing away from the front of the gear housing (9) under the drive motor (7) can be used because of the good accessibility very cheap for a large oil sight glass and oil drain and oil filling. On the long sides, it is advantageous to attach continuous steel profiles for the stable foot / floor support.
- FIG. 3 shows, in a deeper sectional view, the illustration of the course of the oil flow (27) from the transmission oil chamber (29) via the calming and storage oil chamber (31) to the intake oil chamber (30), where, for example, via an intake pipe (28), the oil to the oil pump (12) in Fig. 3 passes.
- the completely continuous partition wall (23) between the transmission oil chamber (29) and the intake oil chamber prevents the highly turbulent oil from entering the intake oil chamber (30) directly from the transmission oil chamber (29).
- the oil calms down, because the air contained in the oil (due to the intensive oil movement in the transmission oil space) can largely escape from the oil.
- the further deflection partitions (26) for generating the longest possible soothing for the oil on the way to the oil suction (28) with the oil passage openings (25) can either be designed directly in the cast of the gear housing (9) or via subsequently inserted separating plates.
- Screw spindle rotor pair as right and left-rising, opposing rotating Verdrängerrotore
- crown or bevel gear drive gear according to WO 01/57401
- Drive motor preferably as a standard / standard motor
- Cooling fan exemplified here as axial fan, if necessary. also radial fan
- Oil pump shown here by way of example as internal gear oil pump, e- benso but also any other known design
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112007001533T DE112007001533A5 (de) | 2006-07-03 | 2007-06-29 | Antrieb für eine Schraubenspindelpumpe 1 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006030982 | 2006-07-03 | ||
DE102006030982.0 | 2006-07-03 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2008003657A1 true WO2008003657A1 (de) | 2008-01-10 |
Family
ID=38508923
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2007/056585 WO2008003657A1 (de) | 2006-07-03 | 2007-06-29 | Antrieb für eine schraubenspindelpumpe |
Country Status (2)
Country | Link |
---|---|
DE (1) | DE112007001533A5 (de) |
WO (1) | WO2008003657A1 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010006663A1 (de) * | 2008-07-18 | 2010-01-21 | Ralf Steffens | Kühlung einer schraubenspindelpumpe |
WO2011077230A3 (en) * | 2009-12-21 | 2012-08-23 | Eaton Corporation | Supercharger timing gear oil pump |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN106767617B (zh) * | 2016-12-22 | 2019-03-19 | 陈曦 | 基于加速度测量的游梁式抽油机光杆位移传感器及方法 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE9013733U1 (de) * | 1990-10-02 | 1991-01-03 | Aerzener Maschinenfabrik GmbH, 3258 Aerzen | Zweiwellige Drehkolbenmaschine |
JPH06346881A (ja) * | 1993-06-07 | 1994-12-20 | Hitachi Ltd | 二段無給油形スクリュー圧縮機 |
WO2001057401A1 (de) * | 2000-02-02 | 2001-08-09 | Ralf Steffens | Antrieb einer schraubenspindelpumpe |
DE10047940A1 (de) * | 2000-06-02 | 2001-12-13 | Hitachi Ltd | Schraubenkompressionsvorrichtung und Verfahren zu deren Betriebssteuerung |
-
2007
- 2007-06-29 WO PCT/EP2007/056585 patent/WO2008003657A1/de active Application Filing
- 2007-06-29 DE DE112007001533T patent/DE112007001533A5/de not_active Withdrawn
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE9013733U1 (de) * | 1990-10-02 | 1991-01-03 | Aerzener Maschinenfabrik GmbH, 3258 Aerzen | Zweiwellige Drehkolbenmaschine |
JPH06346881A (ja) * | 1993-06-07 | 1994-12-20 | Hitachi Ltd | 二段無給油形スクリュー圧縮機 |
WO2001057401A1 (de) * | 2000-02-02 | 2001-08-09 | Ralf Steffens | Antrieb einer schraubenspindelpumpe |
DE10047940A1 (de) * | 2000-06-02 | 2001-12-13 | Hitachi Ltd | Schraubenkompressionsvorrichtung und Verfahren zu deren Betriebssteuerung |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010006663A1 (de) * | 2008-07-18 | 2010-01-21 | Ralf Steffens | Kühlung einer schraubenspindelpumpe |
CN102099583A (zh) * | 2008-07-18 | 2011-06-15 | 拉尔夫·斯蒂芬斯 | 螺杆泵的冷却装置 |
WO2011077230A3 (en) * | 2009-12-21 | 2012-08-23 | Eaton Corporation | Supercharger timing gear oil pump |
US8932033B2 (en) | 2009-12-21 | 2015-01-13 | Eaton Corporation | Supercharger timing gear oil pump |
Also Published As
Publication number | Publication date |
---|---|
DE112007001533A5 (de) | 2009-05-20 |
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