US20120121450A1 - Screw spindle pump arrangement - Google Patents

Screw spindle pump arrangement Download PDF

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Publication number
US20120121450A1
US20120121450A1 US13/262,426 US201013262426A US2012121450A1 US 20120121450 A1 US20120121450 A1 US 20120121450A1 US 201013262426 A US201013262426 A US 201013262426A US 2012121450 A1 US2012121450 A1 US 2012121450A1
Authority
US
United States
Prior art keywords
screw spindle
pump arrangement
connection
high pressure
connecting line
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US13/262,426
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English (en)
Inventor
Robert Eckert
Thorsten Zellmann
Georg Leutgeb
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ZELLMANN, THORSTEN, ECKERT, ROBERT, LEUTGEB, GEORG
Publication of US20120121450A1 publication Critical patent/US20120121450A1/en
Abandoned legal-status Critical Current

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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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps 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
    • F04C2/16—Rotary-piston machines or pumps 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
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/02—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for several machines or pumps connected in series or in parallel
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/185—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by varying the useful pumping length of the cooperating members in the axial direction
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/10—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves

Definitions

  • the invention relates to a screw spindle pump arrangement in accordance with the preamble of patent claim 1 .
  • Screw spindle pumps usually have two or three spindles which are arranged parallel to one another, mesh with one another and are set in rotation by a mobile machine (for example, electric motor).
  • the spindles are received in a housing, there being only minimum spacings between the outer sides of the spindles and the housing.
  • the fluid to be conveyed is conveyed along the spindles in the spaces which result in the helical threads which engage into one another in the manner of a screw thread between the spindles and the housing. This results in a low pressure region at one end of the spindles or the housing and a high pressure region at the other end. At the same time, the fluid to be conveyed penetrates into the minimum spacings between the spindles and the housing and produces a supporting and lubricating film.
  • Document DE 39 20 901 A1 discloses a screw spindle pump having three spindles.
  • a central drive spindle meshes with running spindles which are arranged on both sides and along the helical threads of which a fluid is conveyed.
  • the spindles are not continuously helical, but rather are divided into two sections which are wound in opposite directions and the spaces of which move toward one another during rotation. This results in two low pressure regions at the two ends of the spindles and a high pressure region in the center of the spindles.
  • the invention is based on the object of providing a screw spindle pump arrangement which can be adapted simply to different requirements with regard to pump output pressure and volumetric flow.
  • the screw spindle pump arrangement according to the invention has a high pressure connection, a low pressure connection, a drive spindle and at least one running spindle.
  • a conveying section of the running spindle can be divided into two conveying sections which can be operated or have flow passing through them either in parallel or in series.
  • a screw spindle pump arrangement is provided with low outlay, in which screw spindle pump arrangement two operating states can be selected without regulating technology (higher output pressure with a lower volumetric flow or lower output pressure with a higher volumetric flow).
  • two tapping connections which can be connected by a connecting line are provided on the housing in a central region of the conveying section.
  • the connecting line can be shut off, and it is possible here for the first tapping connection in the conveying direction to be connected to the high pressure connection and for the second tapping connection in the conveying direction to be connected to the low pressure connection.
  • the open connecting line there is a series circuit (higher pressure, lower volumetric flow) which corresponds to a screw spindle pump according to the prior art.
  • the screw spindle pump arrangement can be operated simply in the parallel circuit (lower pressure, higher volumetric flow).
  • the spacing of the two tapping connections along the conveying section corresponds at least to the width of the lands of the running spindles. At least one land therefore prevents an exchange of pressure medium between the regions of the two tapping connections.
  • a directional valve is arranged in the connecting line, which directional valve is connected via a high pressure connecting line to the high pressure connection and via a low pressure connecting line to the low pressure connection.
  • a switchover between series circuit and parallel circuit can thus be carried out by valve actuation.
  • the pressure medium flow path between the tapping connections via the connecting line is preferably shut off in a spring prestressed basic position of a directional valve body. Instead, the first tapping connection is connected to the high pressure connection and the second tapping connection is connected to the low pressure connection. In a switching position of the valve body, in contrast, the two tapping connections are connected to one another via the connecting line.
  • a nonreturn valve is arranged in the high pressure connecting line, which nonreturn valve opens from the directional valve to a high pressure line which connects the high pressure connection to a pump outlet.
  • a pressure limiting valve which relieves to a tank can be arranged on the high pressure line.
  • the pressure limiting valve can be pilot controlled pneumatically.
  • the screw spindle pump arrangement has two running spindles, the threads of which are wound in the same direction.
  • the drive spindle can be driven by a constant two pole electric motor, the manufacturing costs of which are lower than those of a controllable electric motor.
  • the drive spindle can be connected to a speed-controlled electric motor, it being possible for a pressure sensor which is connected to said electric motor to be arranged on the high pressure line.
  • the screw spindle pump arrangement according to the invention is preferably used for supplying a machine tool with cooling lubricant.
  • the switchover possibility according to the invention is particularly advantageous.
  • the series circuit higher pressure with lower volumetric flow
  • the parallel circuit lower pressure with higher volumetric flow
  • FIGURE shows a screw spindle pump arrangement according to the invention. It has a screw spindle pump 1 , the basic construction of which is known from the prior art and which is shown (in the FIGURE) on the left and in section.
  • the screw spindle pump has an elongate housing which consists substantially of a housing main section 2 and two end-side housing covers 3 , 4 .
  • Two running spindles 6 which are at minimum spacings from the adjacent sections of the inner wall 8 of the housing main section 2 are arranged in the interior of the housing 2 , 3 , 4 .
  • the running spindles 6 have circumferentially wound grooves or threads 10 . Likewise circumferentially wound lands 12 remain between the windings of the threads 10 .
  • a drive spindle 14 which likewise has a circumferentially wound land 16 is arranged centrally in the housing main section 2 and between the running spindles 6 .
  • the land 16 is wound in the opposite direction to the lands 12 of the running spindles 6 , the drive spindle 14 meshing with both running spindles 6 .
  • a shaft section 18 is formed at the upper (in the FIGURE) end section of the drive spindle 14 , which shaft section 18 is mounted via an antifriction bearing 20 in the upper (in the FIGURE) housing cover 4 and has a connection section 22 outside the housing 2 , 3 , 4 .
  • the drive spindle 14 can be driven by an electric motor (not shown) via the connection section 22 , it being possible for the electric motor to be a constant motor for cost reasons or to be controllable for reasons of higher flexibility.
  • two tapping connections 28 which are spaced apart axially are provided in the housing main section 2 in a central region of the conveying section which extends from top to bottom (in the FIGURE). Their dimension transversely with respect to the conveying direction is selected in such a way that they have a pressure medium connection to the corresponding thread sections of both running spindles 6 .
  • the two tapping connections 28 , 30 are at an axial spacing from one another in the conveying direction, which axial spacing corresponds at least to the thickness of the lands 16 .
  • the screw spindle pump arrangement according to the invention has a 4/2-way valve 32 .
  • the low pressure connection 24 is connected to the second tapping connection 30 via a low pressure line 34 , a low pressure connecting line 36 and via a second tapping line 38 .
  • the first tapping connection 28 is connected to a high pressure line 44 via a first tapping line 40 and a high pressure connecting line 42 .
  • the high pressure line 44 connects the high pressure connection 26 to a pump outlet P.
  • a switching position (b) of the valve body which switching position (b) can be selected via a switching magnet 46 , a pressure medium flow path from the first tapping connection 28 via the first tapping line 40 , the directional valve 32 and the second tapping line 38 to the second tapping connection 30 is opened.
  • a nonreturn valve 48 which opens from the directional valve 32 to the high pressure line 44 is provided in the high pressure connecting line 42 .
  • the conveying section of the two running spindles 6 can be operated substantially continuously or, as an alternative, can be divided into two conveying sections 45 a , 45 b which can be operated in parallel.
  • the parallel circuit of the two conveying sections 45 a , 45 b is achieved in the switching position (a) (shown in the FIGURE) of the valve body of the directional valve 32 .
  • the pressure medium volumetric flow which is sucked in at a suction connection S is divided firstly via the low pressure line 34 to the low pressure connection 24 and secondly via the low pressure connecting line 36 and the second tapping line 38 to the second tapping connection 30 .
  • the two conveying sections 45 a , 45 b of the running spindles 6 are therefore operated in parallel, a first high pressure volumetric flow flowing from the first tapping connection 28 via the first tapping line 40 and via the high pressure connecting line 42 to the pump outlet P, while a second volumetric flow flows from the high pressure connection 26 via the high pressure line 44 to the pump outlet P.
  • the volumetric flow at the pump outlet P is therefore comparatively high, while the output pressure at the pump outlet P is comparatively low.
  • the series circuit of the two conveying sections 45 a , 45 b and/or conventional operation of the screw spindle pump arrangement according to the invention are/is achieved by the switching magnet 46 having current applied to it and displacing the valve body of the directional valve 32 into the switching position which is labeled by b.
  • the two tapping connections 28 , 30 are connected to one another, the pressure loaded pressure medium flowing out of the first conveying section 45 a via the two tapping lines 40 , 38 into the second conveying section 45 b of the running spindles 6 .
  • the second part of the pressure increase then takes place in the second conveying section 45 b , the pressure medium flowing with maximum pressure out of the high pressure connection 26 via the high pressure line 44 to the pump outlet P.
  • the volumetric flow is comparatively low, while the pressure increase is comparatively high.
  • the nonreturn valve 48 which is arranged in the high pressure connecting line 42 closes in the case of a series circuit of the two conveying sections 45 a , 45 b and opens in the case of a parallel circuit of the two conveying sections 45 a , 45 b if approximately the same pressure prevails in the high pressure connecting line 42 and in the high pressure line 44 .
  • a line 49 branches off from the high pressure line 44 , in which line 49 a pressure limiting valve 50 is provided which, if an adjustable maximum pressure is exceeded, relieves the high pressure line 44 to a tank T.
  • the pressure limiting valve 50 is pilot controlled pneumatically and has an infinitely adjustable proportional pressure valve.
  • an electronic pressure sensor 52 and a manometer 54 for monitoring the pump outlet pressure are provided on the high pressure line 44 , the pressure loading of the manometer 54 taking place via a throttle 56 .
  • the screw spindle pump arrangement according to the invention is particularly suitable for conveying cooling lubricant in machine tools.
  • screw spindle pumps are preferred, since they have the highest possible resistance to partially abrasive particles which accumulate in the cooling lubricant.
  • the maximum drive power of the electric motor (not shown) can be reduced here in the abovementioned use range by approximately 40% with respect to the prior art.
  • the screw spindle pump arrangement according to the invention has the advantage, in addition to the lower costs, that a volumetric flow reduction is not produced by a speed reduction, as a result of which the supporting property of the cooling lubricant could be impaired in the regions between the lands 12 and the housing main section 2 .
  • a screw spindle pump arrangement having a low pressure connection, a high pressure connection, a drive spindle and at least one running spindle.
  • a conveying section of the running spindles can be divided into two conveying sections which can be operated either in parallel or in series.
  • a screw spindle pump arrangement is provided with low outlay, in which screw spindle pump arrangement two operating states can be selected without regulating technology.
  • Two tapping connections which can be connected by a connecting line are provided in a central region of the conveying section.
  • the connecting line can be shut off, and here the low pressure-side tapping connection can be connected to the high pressure connection and the high pressure-side tapping connection can be connected to the low pressure connection.
  • the open connecting line there is a series circuit (higher pressure, lower volumetric flow) which corresponds to a screw spindle pump according to the prior art.
  • the screw spindle pump arrangement can be operated simply in the parallel circuit (lower pressure, higher volumetric flow).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
US13/262,426 2009-03-31 2010-02-23 Screw spindle pump arrangement Abandoned US20120121450A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102009015685.2 2009-03-31
DE102009015685A DE102009015685A1 (de) 2009-03-31 2009-03-31 Schraubenspindelpumpenanordnung
PCT/EP2010/001096 WO2010112108A2 (de) 2009-03-31 2010-02-23 Schraubenspindelpumpenanordnung

Publications (1)

Publication Number Publication Date
US20120121450A1 true US20120121450A1 (en) 2012-05-17

Family

ID=42674932

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/262,426 Abandoned US20120121450A1 (en) 2009-03-31 2010-02-23 Screw spindle pump arrangement

Country Status (5)

Country Link
US (1) US20120121450A1 (de)
JP (1) JP2012522166A (de)
CN (1) CN102449311A (de)
DE (1) DE102009015685A1 (de)
WO (1) WO2010112108A2 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150240810A1 (en) * 2014-02-25 2015-08-27 Leistritz Pumpen Gmbh Screw spindle pump
EP3324048A4 (de) * 2015-07-16 2019-03-27 IHI Corporation Dreifachzahnradpumpe und fluidversorgungsvorrichtung
DE102018130472A1 (de) * 2018-11-30 2020-06-04 Nidec Gpm Gmbh Schraubenspindelpumpe
EP3615805A4 (de) * 2017-04-28 2020-12-30 Atlas Copco Comptec, LLC Gasverarbeitungs- und verwaltungssystem zum umschalten zwischen betriebsarten
CN114165935A (zh) * 2021-12-13 2022-03-11 恩德特机械（苏州）有限公司 一种基于智能化控制的螺杆式冷水机组

Families Citing this family (5)

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Publication number Priority date Publication date Assignee Title
DE102010054401B4 (de) * 2010-12-14 2017-02-02 Grob-Werke Gmbh & Co. Kg Bearbeitungsmaschine
JP7072417B2 (ja) * 2018-03-27 2022-05-20 株式会社日立産機システム スクリュー圧縮機
DE102018116772B3 (de) * 2018-07-11 2019-11-07 Netzsch Pumpen & Systeme Gmbh Schraubenspindelpumpe und Verfahren zur Wartung einer solchen Schraubenspindelpumpe
CN111008480B (zh) * 2019-12-13 2023-05-23 湘潭大学 一种用于离心泵站扩能需求的新增泵选型方法
DE102020122460A1 (de) * 2020-08-27 2022-03-03 Leistritz Pumpen Gmbh Verfahren und Schraubenspindelpumpe zur Förderung eines Gas-Flüssigkeitsgemischs

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150240810A1 (en) * 2014-02-25 2015-08-27 Leistritz Pumpen Gmbh Screw spindle pump
US9765776B2 (en) * 2014-02-25 2017-09-19 Leistritz Pumpen Gmbh Screw spindle pump
EP3324048A4 (de) * 2015-07-16 2019-03-27 IHI Corporation Dreifachzahnradpumpe und fluidversorgungsvorrichtung
US10648467B2 (en) 2015-07-16 2020-05-12 Ihi Corporation Triple gear pump and fluid supplying device
EP3615805A4 (de) * 2017-04-28 2020-12-30 Atlas Copco Comptec, LLC Gasverarbeitungs- und verwaltungssystem zum umschalten zwischen betriebsarten
DE102018130472A1 (de) * 2018-11-30 2020-06-04 Nidec Gpm Gmbh Schraubenspindelpumpe
CN113039346A (zh) * 2018-11-30 2021-06-25 尼得科盖普美有限责任公司 用于冷却电池组的螺杆泵
CN114165935A (zh) * 2021-12-13 2022-03-11 恩德特机械（苏州）有限公司 一种基于智能化控制的螺杆式冷水机组

Also Published As

Publication number Publication date
WO2010112108A3 (de) 2010-11-25
DE102009015685A1 (de) 2010-10-07
JP2012522166A (ja) 2012-09-20
WO2010112108A2 (de) 2010-10-07
CN102449311A (zh) 2012-05-09

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Owner name: ROBERT BOSCH GMBH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:ECKERT, ROBERT;ZELLMANN, THORSTEN;LEUTGEB, GEORG;SIGNING DATES FROM 20111025 TO 20111107;REEL/FRAME:027474/0952

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION