EP1669606A2 - Compresseur à vis - Google Patents

Compresseur à vis Download PDF

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Publication number
EP1669606A2
EP1669606A2 EP05025950A EP05025950A EP1669606A2 EP 1669606 A2 EP1669606 A2 EP 1669606A2 EP 05025950 A EP05025950 A EP 05025950A EP 05025950 A EP05025950 A EP 05025950A EP 1669606 A2 EP1669606 A2 EP 1669606A2
Authority
EP
European Patent Office
Prior art keywords
pressure
lubricant
screw compressor
compressor according
screw
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.)
Granted
Application number
EP05025950A
Other languages
German (de)
English (en)
Other versions
EP1669606B1 (fr
EP1669606A3 (fr
Inventor
Rolf Dieterich
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.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and Co KG
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 Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Publication of EP1669606A2 publication Critical patent/EP1669606A2/fr
Publication of EP1669606A3 publication Critical patent/EP1669606A3/fr
Application granted granted Critical
Publication of EP1669606B1 publication Critical patent/EP1669606B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/16—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using lift valves
    • 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
    • F04C29/021—Control systems for the circulation of the lubricant
    • 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
    • F04C2240/81—Sensor, e.g. electronic sensor for control or monitoring
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/21—Pressure difference
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S418/00—Rotary expansible chamber devices
    • Y10S418/01—Non-working fluid separation

Definitions

  • the invention relates to a screw compressor for compressing refrigerant in a refrigerant circuit, comprising a compressor housing, in which a screw rotor receptacle and an inlet channel and an outlet channel for the refrigerant to be compressed are provided, at least one arranged in the screw rotor receiving screw rotor, a drive for the at least one screw rotor and a lubricant supply which supplies lubricant from a pressurized lubricant reservoir via a line system to at least the at least one screw compressor during operation.
  • the invention is therefore based on the object to improve a screw compressor of the generic type such that the operation and monitoring of the screw compressor made more reliable.
  • a valve is provided, which is controllable by a pressure difference between the pressure in the outlet channel and a reference pressure influenced by a pressure in the refrigerant circuit and in the case of refrigerant screw rotor opens, as well as closes at refrigerant non-compressing screw rotor.
  • a significant advantage of the solution according to the invention is the fact that the valve does not operate on the basis of an absolute pressure, but rather establishes a pressure difference between the pressure in the outlet channel, that is to say the pressure of the compressed refrigerant, and a reference pressure resulting from a pressure in the refrigerant circuit is affected. This means that this makes it possible, regardless of the absolute pressure level at which the screw compressor and the refrigerant circuit work, to detect a proper function of the screw rotor.
  • the reference pressure can be influenced by any pressure in the refrigerant circuit.
  • a particularly simple solution provides that the reference pressure is influenced by a pressure in the high-pressure section of the refrigerant circuit, so that the reference pressure already has a pressure level which is not very different from the pressure level of the compressed refrigerant in the outlet channel.
  • the control of the valve can be designed particularly simple.
  • the reference pressure is derived from a pressure in the high-pressure section of the refrigerant circuit, that is to say is preferably substantially proportional to the pressure in the high-pressure section of the refrigerant circuit.
  • a particularly simple solution provides that the reference pressure is influenced by the pressure in the refrigerant circuit which is transmitted from the lubricant supply and acts on the lubricant reservoir.
  • the valve can be formed in a particularly simple manner if the valve can be controlled by a piston, on which, on the one hand, refrigerant under the pressure in the outlet channel and, on the other hand, the reference pressure act.
  • the valve is preferably formed so that it has a valve seat and a valve body comprising valve assembly which is formed so that when seated on the valve seat on the valve body the valve body acting pressure of the lubricant causes a force in the direction of the closed position of the valve body.
  • valve body is acted upon by an elastic force store, for example a spring, which transfers the valve to its closed position during a pressure compensation on the piston and holds it in this position.
  • an elastic force store for example a spring
  • valve is integrated in the compressor housing of the screw compressor.
  • a lubricant filter is preferably arranged in the line system for the lubricant for the preparation of the lubricant.
  • the lubricant filter is preferably integrated in the compressor housing of the screw compressor to obtain a compact unit.
  • a screw compressor of the type described above in addition or as an alternative to the invention described so far, it comprises a first differential pressure sensing element which detects a pressure difference between the pressure in the outlet channel and a reference pressure influenced by a pressure in the refrigerant circuit, and the screw compressor controls the compressor comprises, which, if the pressure difference after a start-up phase of the drive is not in an operating pressure range defined by compressing the refrigerant, shuts off the drive for the at least one screw rotor.
  • the advantage of the solution according to the invention is to be seen in the fact that it is possible to monitor whether the screw compressor works in the sense of compressing the refrigerant and if this should not be the case, for example if the drive is running in the wrong direction, the drive off.
  • the reference pressure is influenced by a pressure in the high pressure section of the refrigerant circuit, so that thereby there is a reference pressure which is of the same order of magnitude as the pressure in the outlet channel, so that the differential pressure can be determined in a simple manner.
  • the reference pressure is derived from, preferably proportional to, a pressure in the high-pressure section of the refrigerant circuit.
  • the reference pressure could be supplied to the differential pressure sensing element through a separate pressure line between the differential pressure sensing element and the respective section of the refrigerant circuit.
  • a particularly simple solution provides that the reference pressure is influenced by the pressure in the refrigerant circuit transmitted by the lubricant supply and acting on the lubricant reservoir.
  • the differential pressure sensing element comprises an actuating device for the valve in the lubricant supply and an actuating positions of the same detecting sensor.
  • valve can be used directly to respond according to the differential pressure and then its positions can be used to detect the differential pressure.
  • a particularly favorable solution provides that the sensor detects piston positions of the actuating device.
  • the detection of the piston positions can be done in various ways, for example, this inductive or magnetic field-responsive sensors can be used when the piston is provided with a magnet whose position is then detected by the sensor.
  • the compressor control determines the start-up phase of the drive through a time window which defines a certain period of time after the drive has been switched on.
  • the compressor control works in such a way that it checks whether the operating pressure range is reached during the start-up phase, that is to say that the compressor control must receive the signal indicating the operating pressure range at the latest at the end of the start-up phase.
  • the operating pressure range is defined by the fact that the valve has left its closed position.
  • a further advantageous embodiment provides that a second differential pressure sensing element is provided, which detects a pressure difference forming on the lubricant filter and that the compressor control switches off the drive when the pressure difference exceeds a threshold value.
  • a particularly simple solution provides that the differential pressure sensing element detects the pressure of the lubricant in the line system in front of a filter body and after the filter body of the lubricant filter.
  • the differential pressure sensing element is formed so that it comprises a piston which is acted on the one hand by lubricant before passing through the filter body and on the other hand by lubricant after passing through the filter body of the lubricant filter and thus adjusts the piston according to the pressure difference.
  • the differential pressure detection element comprises a sensor for detecting at least one position of the piston.
  • a particularly compact solution provides that the differential pressure sensing element is integrated into the compressor housing, that is, is mounted on this, that it forms part of an overall housing for the screw compressor.
  • An exemplary embodiment of a refrigerant circuit according to the invention designated as a whole by 10 in FIG. 1, comprises a plurality of compressors 12a to 12c connected in parallel, whose high-pressure ports 14a to 14c are connected to a high-pressure line system 16 which leads to a lubricant separator designated as a whole by 18, in which From the high pressure and compressed refrigerant lubricant is deposited.
  • a high-pressure line 20 passes through a heat exchanger 22, which cools the compressed refrigerant, and then to an expansion valve 24, which serves to lower its temperature by releasing the refrigerant, so that the expanded refrigerant in a heat exchanger 26 has the possibility to give up heat again.
  • the expanded refrigerant is passed through a low pressure line 28 to low pressure ports 30a to c of the compressor 12a to c.
  • the compressors 12a, 12b and 12c are arranged in parallel in the refrigerant circuit 10, but can be individually switched on or off, depending on the requested cooling capacity.
  • the parallel-connected compressors 12a, 12b and 12c are supplied with lubricant from a lubricant reservoir 30 forming in the lubricant separator 18 and an external line system 34 originating from the lubricant reservoir, which leads to a lubricant supply connection 36a, 36b and 36c of the respective compressor 12a to 12c ,
  • FIG. 2 An example of such a compressor 12 is shown in FIG. 2, and comprises a compressor housing 40 in which a screw rotor receptacle 42, for example in the form of two screw rotor bores, is provided, which serves to receive two cooperating screw rotors 44, 46.
  • a screw rotor receptacle 42 for example in the form of two screw rotor bores, which serves to receive two cooperating screw rotors 44, 46.
  • the screw rotors 44, 46 engage in each other for compressing the refrigerant, wherein one of the screw rotors, for example the screw rotors 46, is driven by a drive motor 48 as a whole, which is likewise arranged in the compressor housing 40.
  • the drive motor 48 drives a drive shaft 50, on which the screw rotor 46 and a rotor 52 of the drive motor are seated and which is rotatably mounted in the compressor housing 40 about a rotor axis 54.
  • the rotor 52 of the drive motor 48 is driven by the interaction with a stator 56 likewise arranged in the compressor housing 42.
  • the screw compressor is constructed from the basic principle, as described in the European patent application WO 02/053917, to which reference is made in full in this regard.
  • the compressor housing 40 comprises on a side opposite to the drive motor 48 side, a bearing housing 58, in which bearing units 60 and 62 for the storage of screw rotors 44, 46 are arranged.
  • Such a screw compressor is shown again schematically in Fig. 3, wherein for reasons of simplicity of the drive motor 48 and only one screw rotor, namely the screw rotor 46 are shown in its schematic arrangement in the likewise schematically drawn compressor housing.
  • an inlet passage 70 leads to the screw rotors 44 and 46, and further, as shown in FIG. 3, an exhaust passage 72 is provided in the compressor housing 40, leading the compressed refrigerant to the high-pressure port 14 on which a check valve 74 is subsequently arranged, through which the compressed refrigerant enters the high-pressure line system 16 and is then guided to the lubricant separator 18.
  • an internal lubricant line system 80 is provided which, starting from the lubricant supply port 36 through a lubricant filter 82 filtered lubricant on the one hand to the bearings 60, 62 for the screw rotors and on the other hand, the screw rotors 44, 46 to lubricate these during running.
  • a lubricant filter 82 filtered lubricant on the one hand to the bearings 60, 62 for the screw rotors and on the other hand, the screw rotors 44, 46 to lubricate these during running.
  • it can be used to supply the device for power control of the screw compressor with pressurized lubricant.
  • the internal lubricant line system 80 can also be guided to other bearings of the screw rotors 44, 46 and the drive motor 48.
  • the lubricant filter is, as shown in FIGS. 2, 3 and 4, formed by a filter housing 84 integrated in the compressor housing 40, in whose interior space 86 a filter body 88 is inserted, which filters into the interior 86 entering lubricant and a filter body of the 88th enclosed space 90, the filtered lubricant leads to a designated as a whole with 92 lubricant stop valve, which is integrated in a cover body 94 of the filter housing 84 and thus also in the compressor housing 40.
  • the lid body 94 comprises an opening 96 for the lubricant which is open toward the space 90 and is adjoined by a receiving space 100 leading to a valve seat 98 for a valve body 102 of the lubricant stop valve 92.
  • a discharge channel 104 is provided for the filtered and the valve seat 98 by flowing lubricant, starting from the outflow space 104, the further internal lubricant line system 80 continues.
  • the outflow space 104 also passes through a valve body 102 carrying the valve stem 106 which leads from the valve body 102 to a valve piston 108 which separates two arranged in a cylinder housing 110 cylinder chambers 112 and 114 from each other, wherein the cylinder housing 110 also in the lid body 94 of the valve housing 84 is integrated.
  • the cylinder chamber 112 lies on a side facing the valve body 102 and is connected via a branch channel 116 to the outflow channel 104 of the internal lubricant line system 80, so that the piston 108 can be acted upon by lubricant present in the cylinder chamber 112 with a pressure P1.
  • the cylinder chamber 114 is connected via a guided in the compressor housing 40 channel 118 to the outlet channel 72 of the screw compressor 12, so that the piston 108 on the other hand is acted upon by the pressure P2 in the outlet channel 72 standing refrigerant.
  • a piston 120 acting on the spring 108 is provided in the cylinder housing 110, which acts on the piston 108 in the direction of a closed position in which the piston 108 ensures that the valve body 102 rests sealingly on the valve seat 98 and in particular at pressure equalization on Piston 108 keeps the valve closed.
  • the opening and closing of the lubricant stop valve 92 thus takes place by moving the piston 108 in accordance with the pressure difference between the pressure P1 in the cylinder chamber 112 and the pressure P2 in the cylinder chamber 114.
  • the lubricant stop valve opens by the piston 108 moving to the open position against the force of the spring 120 and causing the valve body 102 to lift off the valve seat 98 so that lubricant may enter the discharge channel 104 from the space 90 and from there into the on-going internal lubricant line system 80.
  • the lubricant stop valve 92 has not only the task, when switching off the drive motor 48 and thus the movement of the screw rotors 44 and 46 to interrupt the flow of lubricant from the space 90 of the lubricant filter 82 in the other internal lubricant line 80, but is also part of a first pressure difference detecting element 130th , which additionally comprises a position sensor 132 for the positions of the piston 108.
  • the position sensor 132 is formed, for example, by a so-called reed relay 134 and a reed relay triggering magnetic body 136, which in turn is moved with the piston 108 in the cylinder housing 110.
  • the signal of the position sensor 132 is forwarded to a compressor controller 140, with which also the drive motor 48 is controllable.
  • the differential pressure sensing element 130 now provides not only the ability for the compressor controller 140 to detect whether the lubricant stop valve 92 has opened, but also the ability to detect whether the screw rotors 44, 46 are driven by the drive motor 48 in the correct direction of rotation and thus the intended Build up pressure P2 in outlet channel 72. In the wrong direction of rotation of the screw rotor 44, 46 no pressure is built up in the outlet channel.
  • This pressure in the outlet channel which corresponds to the pressure P2 in the cylinder chamber 112, according to the invention is not absolutely detected, but in relation to the reference pressures P1 and P3, by the pressure in the high pressure section 16, 20 of the refrigerant circuit 10, in particular the pressure in the lubricant separator 18th influenced, preferably proportional to this pressure.
  • the first differential pressure sensing element 130 it is possible to determine whether the pressure P2 in the outlet passage 72 is greater than the pressures P1 and P3 and to determine whether the pressure P2 is so high that refrigerant compressed to high pressure through the check valve 74 into the High-pressure line system 16 is promoted.
  • the compressor control 140 is preferably designed so that it observes the position sensor 132 within a time window after switching on the drive motor 148 and checks whether the piston 108 has left the closed position.
  • the time window is set to last a maximum of one second.
  • the time window can also be made even shorter, for example, half a second.
  • the compressor controller 140 If it is detected within the time window by the compressor controller 140 that the piston 108 has not left the closed position, the compressor controller 140 assumes that the screw rotors 44, 46 either rotate in the wrong direction or are otherwise damaged, causing the drive motor to be shut off 48 leads.
  • a second differential pressure sensing element 150 is provided, which, as shown in FIGS. 4 to 7, comprises a cylinder housing 152 in which a Piston 154 is provided, which separates a first cylinder chamber 156 from a second cylinder chamber 158, which are arranged on opposite sides of the piston 154.
  • the first cylinder chamber 156 is acted upon by the pressure P1, which also corresponds approximately to the pressure in the first cylinder chamber 112, while the second cylinder chamber 158 is acted upon by a pressure P4, the pressure of the lubricant in the interior space 86 of the filter housing 84 before passing through the Filter body 88 corresponds.
  • the piston 154 now moves in accordance with the difference between the pressures P 1 and P 4, the piston 154 additionally being acted upon in the direction of its end position corresponding to the correct lubricant flow shown in FIGS. 4 and 5, that is to say the sum of the forces exerted by the spring 160 and the pressure P1 applied to the piston 154 is greater than the force exerted by the pressure P4 on the piston 154.
  • the correct lubricant flow indicating position of the piston 154 is thus dependent on proper operation of the filter cartridge 88 and also dependent on the lubricant stop valve 92 being open at all.
  • a second position sensor 162 which is also designed as a reed contact 164 and detects the position of a magnet 166 entrained by the piston 154 when the piston 154 is in its correct oil flow position.
  • the position sensor 162 is connected to the compressor controller 140 so as to be able to check the correct flow of lubricant through the second differential pressure sensing element 150 and, if necessary, shut off the drive motor in the event of improper lubricant flow, damage due to insufficient lubrication of the screw rotors 44 , 46 or the bearings 60, 62 to avoid.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP05025950.6A 2004-12-02 2005-11-29 Compresseur à vis Active EP1669606B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102004060596A DE102004060596A1 (de) 2004-12-02 2004-12-02 Schraubenverdichter

Publications (3)

Publication Number Publication Date
EP1669606A2 true EP1669606A2 (fr) 2006-06-14
EP1669606A3 EP1669606A3 (fr) 2012-09-05
EP1669606B1 EP1669606B1 (fr) 2014-07-30

Family

ID=35991346

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05025950.6A Active EP1669606B1 (fr) 2004-12-02 2005-11-29 Compresseur à vis

Country Status (5)

Country Link
US (1) US7547203B2 (fr)
EP (1) EP1669606B1 (fr)
CN (1) CN100567742C (fr)
DE (1) DE102004060596A1 (fr)
ES (1) ES2510467T3 (fr)

Cited By (1)

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US10941770B2 (en) 2010-07-20 2021-03-09 Trane International Inc. Variable capacity screw compressor and method

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US20080056887A1 (en) * 2006-06-09 2008-03-06 Entire Interest Hydraulic gear motor with integrated filter
DE102008013784B4 (de) * 2007-03-15 2017-03-23 Denso Corporation Kompressor
BE1019178A3 (nl) * 2010-02-10 2012-04-03 Atlas Copco Airpower Nv Inrichting en werkwijze voor het comprimeren van gas.
US20150030490A1 (en) * 2010-07-20 2015-01-29 Trane International Inc. Bearing Housing and Assembly of a Screw Compressor
US10125752B1 (en) 2012-07-19 2018-11-13 Hydro-Gear Limited Partnership Hydraulic motor
DE102014114837A1 (de) * 2014-10-13 2016-04-14 Bitzer Kühlmaschinenbau Gmbh Kältemittelverdichter
US9915265B2 (en) * 2014-12-31 2018-03-13 Ingersoll-Rand Company Compressor system with variable lubricant injection orifice
US10941775B2 (en) * 2017-12-28 2021-03-09 Ingersoll-Rand Industrial U.S., Inc. Compressor stop valve and associated system
EP3742069B1 (fr) * 2019-05-21 2024-03-20 Carrier Corporation Appareil de réfrigération et utilisation associée
EP3742077B1 (fr) * 2019-05-21 2023-08-16 Carrier Corporation Appareil de réfrigération et utilisation associée
ES2912000T3 (es) * 2019-05-21 2022-05-24 Carrier Corp Aparato de refrigeración y uso del mismo

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Cited By (4)

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Publication number Priority date Publication date Assignee Title
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
US11933301B2 (en) 2010-07-20 2024-03-19 Trane International Inc. Variable capacity screw compressor and method

Also Published As

Publication number Publication date
EP1669606B1 (fr) 2014-07-30
EP1669606A3 (fr) 2012-09-05
US20060117790A1 (en) 2006-06-08
ES2510467T3 (es) 2014-10-21
DE102004060596A1 (de) 2006-06-22
CN100567742C (zh) 2009-12-09
US7547203B2 (en) 2009-06-16
CN1782431A (zh) 2006-06-07

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