US20080085207A1 - Oil-flooded screw compressor with axial-thrust balancing device - Google Patents

Oil-flooded screw compressor with axial-thrust balancing device Download PDF

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Publication number
US20080085207A1
US20080085207A1 US11/801,187 US80118707A US2008085207A1 US 20080085207 A1 US20080085207 A1 US 20080085207A1 US 80118707 A US80118707 A US 80118707A US 2008085207 A1 US2008085207 A1 US 2008085207A1
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US
United States
Prior art keywords
pressure
oil
balancing piston
regulating device
screw compressor
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
US11/801,187
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English (en)
Inventor
Dieter Mosemann
Dmytro Zaytsev
Ottomar Neuwirth
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.)
MOSEMANN DR DIETER
Original Assignee
MOSEMANN DR DIETER
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 MOSEMANN DR DIETER filed Critical MOSEMANN DR DIETER
Assigned to MOSEMANN, DR. DIETER reassignment MOSEMANN, DR. DIETER ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: NEUWIRTH, OTTOMAR, ZAYTSEV, DR. DMYTRO
Publication of US20080085207A1 publication Critical patent/US20080085207A1/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
    • 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
    • F01C21/02—Arrangements of bearings
    • 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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump

Definitions

  • the invention relates to an arrangement on oil-flooded screw compressors with two rotors, a male rotor having essentially convex lobe flanks and a female rotor having essentially concave flank portions, with a rotating disk, the balancing piston, arranged on a shaft section of the male rotor for balancing the axial thrust and sealing contactlessly and being loaded by pressurized oil which is drained to areas of lower pressure after passing the sealing gap of the balancing piston and which counteracts the gas force on the male rotor in axial direction.
  • Both rotors are enclosed in housing sections.
  • the profile sections of the rotors have shaft shoulders enclosed in radial bearings with the axial forces being supported by axial bearings.
  • the gas force acting in axial direction of the rotors is comparatively high at the male rotor compared to the female rotor.
  • the male rotor features a balancing piston.
  • the force on the axial bearing of the male rotor is a resultant from the difference of the gas force acting on the rotor and from the unloading force acting on the balancing piston.
  • the working space designated also as working chamber is formed by the interlobe spaces of both rotors, adjacent housing sections and other adjacent components such as a control slide. Depending on the position of the control slide circumferential wall portions of the cylindrical sections enclosing the rotors are opened.
  • the resultant from the difference of the gas force acting on the rotor and from the unloading force acting on the balancing piston will change.
  • the resultant will act in one or the other direction depending on the operational condition of the compressor.
  • the axial bearings will be loaded more or less in one or the other direction.
  • the unloading force can also considerably exceed the gas force on the male rotor. For this reason, the unloading action of the balancing piston during part-load operation of the compressor is cut off in a known technical solution.
  • a disadvantage is that in this case the entire gas force in a greater part-load region will act on the axial bearings, thus shortening impermissibly the service life of the axial bearings.
  • the object of the invention is to prevent the disadvantages mentioned and to create an arrangement on a screw compressor enabling the bearing loads to be held on a constant low level.
  • the oil pressure on the balancing piston, and hence the unloading force of the balancing piston is controlled depending on operating parameters.
  • the output signal of a regulating device preferably controls the pressure on the balancing piston depending on the driving torque at the compressor drive shaft and depending on the pressure on the compressor suction side.
  • the output signal of the regulating device in a first arrangement according to the invention acts on a pressure-regulating valve located in an oil-supply line from a pressure source to the balancing piston.
  • the control algorithm is designed so that the pressure on the balancing piston will increase when the driving torque rises or when the pressure on the suction side rises or when in combination of rising driving torque and rising pressure on the suction side there will occur changes.
  • there exists a control algorithm considering these parameters and calculating the required pressure on the balancing piston.
  • the means for realization of this control task represent a regulating device into which the speed of rotation to be expected, e.g. 49 1/s, the electric voltage of a three-phase asynchronous motor, e.g. 380 V, the cos ⁇ , e.g. 0,93, and the electrical efficiency of the electric motor, e.g. 0,95, have been entered manually, or are metrologically registered during operation, analogue inputs for registration of the motor current, for registration of the pressure on the compressor suction side, as well as an output with an analogue signal representing the desired pressure on the balancing piston.
  • a regulating device into which the speed of rotation to be expected, e.g. 49 1/s, the electric voltage of a three-phase asynchronous motor, e.g. 380 V, the cos ⁇ , e.g. 0,93, and the electrical efficiency of the electric motor, e.g. 0,95, have been entered manually, or are metrologically registered during operation, analogue inputs for registration of the motor current
  • Voltage, cos ⁇ , efficiency and motor current serve in the algorithm of the regulating device first to determine the power at the compressor drive shaft, and in connection with the speed of rotation the torque will be calculated.
  • the entire control algorithm considers the pressure on the compressor suction side during calculation of the output signal.
  • the output in a preferable arrangement according to the invention has a control interconnection to a pressure-regulating valve, e.g. a proportional pressure-regulating valve, with the flow rate being modulated by changing the output signal of the regulating device.
  • a pressure-regulating valve e.g. a proportional pressure-regulating valve
  • the regulating device incorporates the control algorithm for calculation of the required pressure on the balancing piston and the presentation of this value in the range of a standard signal, e.g. from 4 to 20 mA, or directly as control current for a proportional pressure-regulating valve.
  • a pressure-measuring point is located in the supply line between the pressure-regulating valve and the connection for admission of pressure to the balancing piston.
  • the output signal of the regulating device and the output signal of the pressure-measuring point are led to a three-position controller and compared.
  • the proportional pressure-regulating valve will be opened more, when the pressure at the pressure-measuring point lies below the calculated value of the regulating device, or will be closed more, when the pressure at the pressure-measuring point exceeds the calculated value of the regulating device.
  • a speed controlled oil pump is located in the supply line for admission of pressure to the balancing piston.
  • the speed of the oil pump will be increased, when the pressure at the pressure-measuring point lies below the calculated value of the regulating device, or will be decreased further, when the pressure at the pressure-measuring point exceeds the calculated value of the regulating device.
  • FIG. 1 an arrangement according to the invention with a pressure-regulating valve controllable by an input signal
  • FIG. 2 another arrangement according to the invention with a pressure-regulating valve controllable by a three-position controller.
  • the screw compressor according to the arrangement pursuant to the patent ( FIG. 1 ) is driven at the drive-shaft end 5 forming a fixed part of the male rotor 2 via a coupling not shown.
  • the interlobe spaces of the male rotor 2 and of the female rotor 3 form working chambers to which on the suction side adjoin inlet ports 6 . Due to rotation of the rotors at the drive-shaft end 5 , the volume of an interlobe space considered changes.
  • Radial bearings 1 are arranged on the suction side of the shaft shoulders, while radial bearings 9 and axial bearings 10 are arranged on the discharge side of the shaft shoulders.
  • the balancing piston 11 For compensation of the axial thrust on the male rotor 2 exerted by the gas force due to compression of the working fluid, a rotating disk, the balancing piston 11 , is arranged sealing hydraulically and contactlessly at its external diameter. On one side, it is loaded with pressurized oil directly coming from the oil separator arranged on the discharge side, or the oil is brought up to a higher pressure by an oil pump. On the other side of the balancing piston, there is nearly suction pressure. Thus, the force of the balancing piston 11 counteracts the gas force on the male rotor 2 in axial direction. As a result, the axial bearings 10 are unloaded. According to the embodiment of the invention shown the regulating device 12 is arranged as part of a controlled system.
  • the control algorithm calculates the pressure on the balancing piston 11 depending on the pressure on the compressor suction side and on the torque at the drive-shaft end 5 (essentially from motor current in connection with both motor voltage and speed entered). Pressure and motor current are passed over to the control at the interfaces 13 , 14 .
  • the regulating device 12 delivers the output signal 16 for the proportional pressure-regulating valve 17 . According to the control characteristics of the proportional pressure-regulating valve 17 , there is a proportional relationship between the input signal and the pressure at the outlet of the proportional pressure-regulating valve 17 . It increases the pressure on the balancing piston 11 in case the regulating device 12 has calculated this from the algorithm and given a corresponding output signal. It decreases the pressure on the balancing piston 11 when the regulating device 12 calculates a lower pressure for the balancing piston.
  • a pressure-measuring point 18 is located in the supply line between the proportional pressure-regulating valve 17 and the connection for admission of pressure to the balancing piston.
  • the output signal of the regulating device 12 and the output signal 19 of the pressure-measuring point 18 are led to a three-position controller preferably arranged in the regulating device 12 and compared.
  • the proportional pressure-regulating valve 17 will be opened more, when the pressure at the pressure-measuring point 18 lies below the calculated value of the regulating device 12 , or will be closed more, when the pressure at the pressure-measuring point 18 exceeds the calculated value of the regulating device 12 .

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
US11/801,187 2006-10-10 2007-05-09 Oil-flooded screw compressor with axial-thrust balancing device Abandoned US20080085207A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006047891A DE102006047891A1 (de) 2006-10-10 2006-10-10 Ölüberfluteter Schraubenverdichter mit Axialkraftentlastungseinrichtung
DE102006047891.6 2006-10-10

Publications (1)

Publication Number Publication Date
US20080085207A1 true US20080085207A1 (en) 2008-04-10

Family

ID=39184788

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/801,187 Abandoned US20080085207A1 (en) 2006-10-10 2007-05-09 Oil-flooded screw compressor with axial-thrust balancing device

Country Status (4)

Country Link
US (1) US20080085207A1 (ja)
JP (1) JP2008095684A (ja)
DE (1) DE102006047891A1 (ja)
RU (1) RU2007135649A (ja)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080031762A1 (en) * 2006-08-01 2008-02-07 Dieter Mosemann Screw compressor for extremely high working pressure
US20150098853A1 (en) * 2012-05-25 2015-04-09 Ateliers Busch Sa Screw-type positive displacement machine
CN104879271A (zh) * 2015-04-20 2015-09-02 江苏大学 一种双螺杆高压余能回收装置
WO2019183262A1 (en) * 2018-03-21 2019-09-26 Johnson Controls Technology Company Systems and methods for enhanced compressor bearing life
US10941770B2 (en) 2010-07-20 2021-03-09 Trane International Inc. Variable capacity screw compressor and method
CN112796998A (zh) * 2021-02-26 2021-05-14 珠海格力电器股份有限公司 转子组件、压缩机和空调
WO2021231600A1 (en) * 2020-05-13 2021-11-18 Johnson Controls Technology Company Damping system for compressor
US11209002B2 (en) 2017-09-06 2021-12-28 Joy Global Surface Mining Inc Lubrication system for a compressor
US11680588B2 (en) 2020-04-21 2023-06-20 Joy Global Surface Mining Inc Lubrication system for a compressor
US11725658B2 (en) 2016-08-02 2023-08-15 Johnson Controls Air Conditioning And Refrigeration (Wuxi) Co., Ltd. Screw compressor with male and female rotors
CN118128756A (zh) * 2024-05-08 2024-06-04 德耐尔节能科技（上海）股份有限公司 一种具有轴向平衡装置的螺杆空压机

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021003198A1 (de) 2021-06-22 2022-12-22 Gea Refrigeration Germany Gmbh Schraubenverdichter

Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US146416A (en) * 1874-01-13 Improvement in nut-locks
US3275226A (en) * 1965-02-23 1966-09-27 Joseph E Whitfield Thrust balancing and entrapment control means for screw type compressors and similardevices
US3811805A (en) * 1972-05-16 1974-05-21 Dunham Bush Inc Hydrodynamic thrust bearing arrangement for rotary screw compressor
US4180089A (en) * 1977-09-30 1979-12-25 Ingersoll-Rand Company Thrust piston biasing means
US4462769A (en) * 1981-12-02 1984-07-31 Sullair Technology Ab Method at an oil-injected screw-compressor
US4842501A (en) * 1982-04-30 1989-06-27 Sullair Technology Ab Device for controlling the internal compression in a screw compressor
US4964790A (en) * 1989-10-10 1990-10-23 Sundstrand Corporation Automatic regulation of balancing pressure in a screw compressor
US5018948A (en) * 1987-10-15 1991-05-28 Svenska Rotor Maskiner Ab Rotary displacement compressor with adjustable outlet port edge
US5207568A (en) * 1991-05-15 1993-05-04 Vilter Manufacturing Corporation Rotary screw compressor and method for providing thrust bearing force compensation
US5281115A (en) * 1990-02-09 1994-01-25 Svenska Rotor Maskiner Ab Rotary screw machine having thrust balancing means
US5411388A (en) * 1991-11-13 1995-05-02 Svenska Rotor Maskiner Ab Rotary screw machine with thrust balanced bearings
US5678987A (en) * 1993-10-14 1997-10-21 Svenska Rotor Maskiner Ab Rotary screw compressor with variable thrust balancing means
US6059551A (en) * 1996-10-25 2000-05-09 Kabushiki Kaisha Kobe Seiko Sho Oil injected screw compressor with thrust force reducing means
US6089381A (en) * 1997-05-06 2000-07-18 Gordon; Ellison Oil and gas well separation apparatus
US6551084B2 (en) * 1999-11-11 2003-04-22 Svenska Rotor Maskiner Ab Screw rotor machine having means for axially biasing at least one of the rotors

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US146416A (en) * 1874-01-13 Improvement in nut-locks
US3275226A (en) * 1965-02-23 1966-09-27 Joseph E Whitfield Thrust balancing and entrapment control means for screw type compressors and similardevices
US3811805A (en) * 1972-05-16 1974-05-21 Dunham Bush Inc Hydrodynamic thrust bearing arrangement for rotary screw compressor
US4180089A (en) * 1977-09-30 1979-12-25 Ingersoll-Rand Company Thrust piston biasing means
US4462769A (en) * 1981-12-02 1984-07-31 Sullair Technology Ab Method at an oil-injected screw-compressor
US4842501A (en) * 1982-04-30 1989-06-27 Sullair Technology Ab Device for controlling the internal compression in a screw compressor
US5018948A (en) * 1987-10-15 1991-05-28 Svenska Rotor Maskiner Ab Rotary displacement compressor with adjustable outlet port edge
US4964790A (en) * 1989-10-10 1990-10-23 Sundstrand Corporation Automatic regulation of balancing pressure in a screw compressor
US5281115A (en) * 1990-02-09 1994-01-25 Svenska Rotor Maskiner Ab Rotary screw machine having thrust balancing means
US5207568A (en) * 1991-05-15 1993-05-04 Vilter Manufacturing Corporation Rotary screw compressor and method for providing thrust bearing force compensation
US5411388A (en) * 1991-11-13 1995-05-02 Svenska Rotor Maskiner Ab Rotary screw machine with thrust balanced bearings
US5678987A (en) * 1993-10-14 1997-10-21 Svenska Rotor Maskiner Ab Rotary screw compressor with variable thrust balancing means
US6059551A (en) * 1996-10-25 2000-05-09 Kabushiki Kaisha Kobe Seiko Sho Oil injected screw compressor with thrust force reducing means
US6089381A (en) * 1997-05-06 2000-07-18 Gordon; Ellison Oil and gas well separation apparatus
US6551084B2 (en) * 1999-11-11 2003-04-22 Svenska Rotor Maskiner Ab Screw rotor machine having means for axially biasing at least one of the rotors

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7753665B2 (en) 2006-08-01 2010-07-13 Grasso Gmbh Refrigeration Technology Screw compressor for working pressures above 80 bar
US20080031762A1 (en) * 2006-08-01 2008-02-07 Dieter Mosemann Screw compressor for extremely high working pressure
US11933301B2 (en) 2010-07-20 2024-03-19 Trane International Inc. Variable capacity screw compressor and method
US10941770B2 (en) 2010-07-20 2021-03-09 Trane International Inc. Variable capacity screw compressor and method
US11022117B2 (en) 2010-07-20 2021-06-01 Trane International Inc. Variable capacity screw compressor and method
US11486396B2 (en) 2010-07-20 2022-11-01 Trane International Inc. Variable capacity screw compressor and method
US20150098853A1 (en) * 2012-05-25 2015-04-09 Ateliers Busch Sa Screw-type positive displacement machine
CN104879271A (zh) * 2015-04-20 2015-09-02 江苏大学 一种双螺杆高压余能回收装置
US11725658B2 (en) 2016-08-02 2023-08-15 Johnson Controls Air Conditioning And Refrigeration (Wuxi) Co., Ltd. Screw compressor with male and female rotors
US11209002B2 (en) 2017-09-06 2021-12-28 Joy Global Surface Mining Inc Lubrication system for a compressor
WO2019183262A1 (en) * 2018-03-21 2019-09-26 Johnson Controls Technology Company Systems and methods for enhanced compressor bearing life
CN112041562A (zh) * 2018-03-21 2020-12-04 江森自控科技公司 用于延长压缩机轴承寿命的系统和方法
US11680588B2 (en) 2020-04-21 2023-06-20 Joy Global Surface Mining Inc Lubrication system for a compressor
WO2021231600A1 (en) * 2020-05-13 2021-11-18 Johnson Controls Technology Company Damping system for compressor
US20230175511A1 (en) * 2020-05-13 2023-06-08 Johnson Controls Tyco IP Holdings LLP Damping system for compressor
US12018689B2 (en) * 2020-05-13 2024-06-25 Tyco Fire & Security Gmbh Damping system for compressor
CN112796998A (zh) * 2021-02-26 2021-05-14 珠海格力电器股份有限公司 转子组件、压缩机和空调
EP4239198A4 (en) * 2021-02-26 2024-05-22 Gree Electric Appliances, Inc. of Zhuhai ROTOR, COMPRESSOR AND AIR CONDITIONER ASSEMBLY
CN118128756A (zh) * 2024-05-08 2024-06-04 德耐尔节能科技（上海）股份有限公司 一种具有轴向平衡装置的螺杆空压机

Also Published As

Publication number Publication date
DE102006047891A1 (de) 2008-04-17
RU2007135649A (ru) 2009-04-10
JP2008095684A (ja) 2008-04-24

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Legal Events

Date Code Title Description
AS Assignment

Owner name: MOSEMANN, DR. DIETER, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:ZAYTSEV, DR. DMYTRO;NEUWIRTH, OTTOMAR;REEL/FRAME:019461/0424

Effective date: 20070503

STCB Information on status: application discontinuation

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