EP0060639A1 - Schraubenverdichter - Google Patents

Schraubenverdichter Download PDF

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Publication number
EP0060639A1
EP0060639A1 EP82301011A EP82301011A EP0060639A1 EP 0060639 A1 EP0060639 A1 EP 0060639A1 EP 82301011 A EP82301011 A EP 82301011A EP 82301011 A EP82301011 A EP 82301011A EP 0060639 A1 EP0060639 A1 EP 0060639A1
Authority
EP
European Patent Office
Prior art keywords
fluid
working chamber
compressor
casing
inlet
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.)
Withdrawn
Application number
EP82301011A
Other languages
English (en)
French (fr)
Inventor
Sidney John Morris
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.)
Compair Industrial Ltd
Original Assignee
Compair Industrial Ltd
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 Compair Industrial Ltd filed Critical Compair Industrial Ltd
Publication of EP0060639A1 publication Critical patent/EP0060639A1/de
Withdrawn legal-status Critical Current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
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels

Definitions

  • This invention relates to a meshing screw type compressor.
  • Meshing screw type compressors comprising a casing, a fluid inlet and a fluid outlet, the casing having a working chamber defined therein, the working chamber being periodically in fluid communication with the inlet and outlet and situated therebetween, the fluid being compressed within the working chamber under the interaction of meshing screws therein in passing from the inlet to the outlet, are herein referred to as compressors "of the kind described".
  • a meshing screw compressor of the kind described is commonly matched with a suitable motor running at a prescribed fixed speed, the motor being directly coupled to one of the compressor screws. It is to be expected that a wide variety of compressor applications will be required at a prescribed fixed speed for which the power input requirement will be different for different discharge pressure conditions and the problem then is to find, for a particular duty, a suitable power match between a selected compressor and one of a standard range of motors.
  • British Patent Specification No. 1518271 describes a method for increasing the compression ratio of a standard compressor without any substantial increase in power input requirement.
  • the inlet port of the compressor is enlarged, the enlarged portion extending into the compression zone of the compression chamber to reduce the volumetric capacity of the compressor and hence increase its compression ratio.
  • the modification can be carried out by a cutting operation performed on a standard compressor, the cutting operation becoming increasingly complex the greater the increase in compression ratio is required.
  • the size of the outlet port can be reduced for achieving the maximum increase in compression ratio.
  • the cutting operation can be replaced by making adjustments to the casting model of standard compressors.
  • the method described can be costly and of necessity involves irrevocably modifying a standard compressor, the technique further being unsuitable for providing compressors with a diverse range of output characteristics without a costly variety of production.
  • a compressor of the kind described has means whereby its input power requirement can be reduced to provide an energy saving for its drive motor during the idling operation and in the start-up procedure of the compressor.
  • the means comprises a port or ports in the compression chamber of the compressor, operable by means of one or more shut-off devices, for the passage of fluid from the compression chamber back to the inlet chamber, or to the free atmosphere.
  • the port or ports can be opened during the start-up procedure or in the idling operation of the compressor allowing a substantially uncompressed volume of fluid to be released from the working chamber thereby reducing the power consumption of the compressor.
  • the ports are closed during normal running of the compressor.
  • Compressors built according to this known design involve a substantial increase in manufacturing costs over standard compressor designs without providing any greater variety of fluid output capacities obtainable from a range of compressors available as standard.
  • a comrressor of the kind described having means by which its volumetric capacity can be adjusted whilst being driven at a fixed rotational speed by a motor.
  • the means comprises a number of by-pass channels situated in the compression chamber which provide adjustable communication between the compression chamber and the inlet chamber of the compressor by means of control valves associated with the by-pass channels.
  • the amount of fluid being bled off the compression chamber through the by-pass channels, and hence the volumetric capacity of the compressor can be adjusted by either automatic or manual activation of the control valves.
  • Compressors built to this design necessarilyrinvolve complex production techniques associated with high manufacturing costs.
  • a meshing screw compressor comprising a casing, a fluid inlet and a fluid outlet, the casing . having a working chamber defined therein, the working chamber being periodically in fluid communication with the inlet and the outlet and situated therebetween, the fluid being compressed within the working chamber under the interaction of meshing screws therein in passing from the inlet to the outlet, characterised in that the casing has discharge means therein in permanently open fluid communication with the working chamber to allow fluid to bleed from the working chamber through the discharge means between the inlet and the outlet, in which the discharge means is prearranged to provide a fixed rate of fluid bleed from the working chamber at a constant running speed of the compressor.
  • the discharge means may comprise an opening in a wall of the casing having closure means associated therewith for determining a fixed rate of fluid bleed from the working chamber at a constant running speed of the compressor.
  • the closure means may comprise an insert having a hole therethrough, the insert being received within the opening so that the hole therein is in fluid communication with the working chamber, the fixed rate of fluid bleed.from the working chamber at a constant running speed of the compressor being determined by the size of the hole in the insert.
  • the closure means may comprise a plug mounted on.the casing adjacent the opening, the fixed rate. of fluid bleed from the working chamber at a constant running speed of-the compressor being determined by the gap between the plug and the opening.
  • the closure means may comprise a plug mounted on the casing adjacent the opening, the plug having a portion thereof which extends into the opening, the fixed rate of fluid bleed from the working chamber at a constant running speed of the compressor being determined by the annular clearance between said portion of the plug and the opening.
  • the discharge means is preferably in fluid communication with the fluid inlet so that fluid bleeding off the working chamber, in use, passes from the working chamber back to the fluid inlet.
  • a passageway is preferably formed integrally within a wall of the casing, the passageway being in fluid communication between the discharge means and the fluid inlet to allow fluid bleeding off the working chamber, in use, to pass through the passageway back to the inlet.
  • the discharge means is preferably situated adjacent the fluid inlet end of the working chamber so that fluid bleeding off the working chamber, in use, has not been substantially compressed.
  • Figures 1 , 2 and 3 show a compressor having a casing 10 in which is defined a working chamber 11.
  • a pair of meshing screws is situated in the working chamber 11 and one of the meshing screws is coupled to a motor which thereby drives the compressor.
  • Fluid enters the working chamber 11 from a fluid inlet 12, with or without the use of fluid injection, and is compressed under the interaction of the meshing screws within the working chamber 11. The compressed fluid then passes out through a fluid outlet 13.
  • a fluid discharge arrangement 14 is provided in a wall of the casing 10, in permanently open fluid communication with the working chamber 11, to allow fluid to bleed from the working chamber 11 in use.
  • a passageway 15, formed integrally in the casing 10, intercommunicates the discharge arrangement 14 with the fluid inlet 12 so that fluid bleeding from the working chamber 11 returns to the fluid inlet 12 in use.
  • the passageway 15 can be formed circumferentially on the casing 10 for communication with a fluid inlet 12 positioned on the top of the casing 10 as shown in Figure 2.
  • the passageway 15 can be formed axially on the casing 10 for communication with a fluid inlet 12 -positioned at the end of the casing 10, as shown in Figure 3.
  • discharge arrangment 14 is situated towards the fluid inlet end of the working chamber 11 in order that the fluid bleeding from the working chamber 11, in use, has not been substantially compressed.
  • a hole 16 is drilled through the casing 10 to provide permanently open fluid communication between the working chamber 11 and the passageway 15.
  • This hole 16 is conveniently drilled from the outside of the casing 10 and the hole 17 thereby formed in the outer wall 18 of the passageway 15 is plugged to seal off the passageway . 15 from the free atmosphere.
  • the hole 17 is shown as a tapped hole in which is received a threaded plug 19, but it will be appreciated that other forms of plugging the hole 17 could be employed.
  • the rate of fluid bleed from the working chamber at a constant running speed of the compressor is determined by appropriate selection of the size of the hole 16 in the casing 10.
  • a hole 20 is drilled into the casing 10 to interconnect the passageway 15 with the working chamber 11.
  • the hole 20 is tapped to receive a threaded insert 21.
  • the insert 21 has a hole 22 therethrough for providing permanently open intercommunication between the working chamber 11 and the passageway 15 when the insert 21 is received in the hole 22.
  • the hole 20 is conveniently drilled from the outside of the casing 10, the hole 23 thereby formed in the outer wall 18 of the passageway 15 being plugged to seal off the passageway.15 from the free atmosphere.
  • the hole can be plugged in a number of ways as previously mentioned with reference to Figure 4.
  • the rate of fluid bleed from the working chamber at a constant running speed of the compressor is determined by appropriate selection of the size of the hole 22 in the insert 21.
  • a hole 24 is drilled into the casing 10 to provide permanently open fluid communication between the passageway 15 and the working chamber 11.
  • the hole 24 is again conveniently drilled from the outside of the casing 10, thereby forming a hole 25 in the outer wall 18 of the passageway 15.
  • a plug 26 having a threaded flange at one end and a smaller diameter plain shank at the other is received within the hole 25.
  • the hole 25 has a plain bore portion 27 which is dimensioned to suit the shank of the plug 26, and a counterbored and tapped portion 28 in which the threaded flange of the plug 26 is threadedly received.
  • a washer 29 is interposed between a seat in the hole 25, formed at the junction of the two portions of the hole 25, and the shoulder of the flanged portion of the plug 26.
  • the end of the plain shank of the plug 26 is chamfered and is disposed adjacent the hole 24 which intercommunicates the working chamber 11 with the passageway 15.
  • the rate of fluid bleed from the working chamber 11 to the passageway 15 at a constant running speed of the compressor in this embodiment shown in Figure 6, is determined by the proximity of the chamfered end of the plug shank relative to the hole 24. It will be understood that by inserting washers of different thickness into the hole 25, the proximity of the chamfered end of the plug shank relative to the hole 24 can be altered for selection of a desired bleed rate. Alternatively or additionally, plugs having shanks of different lengths could be employed for this purpose without the need of a washer.
  • a hole 32 is drilled into the casing 10 to provide permanently open fluid communication between the passageway 15 and the working chamber 11.
  • the hole 32 is again conveniently drilled from the outside of the casing 10, thereby forming a hoe 31 in the outer wall 18 of the passageway 15.
  • the hole 31 is tapped to receive a plug 33.
  • the plug 33 has a threaded flange at one end which is threadedly received in the hole 31 and a smaller diameter plain shank 34 at the other end which extends into the hole 32.
  • the rate of fluid bleed from the working chamber 11 to the passageway 15 at a constant running speed of the compressor in this embodiment, shown in Figure 7, is determined by the annular clearance between the plug shank 34 and the hole 32.
  • the plug shank 34 need not necessarily have a circular cross-section but it is important that the plug shank 34 in the embodiment does not extend into the working chamber 11 and hencefoul the meshing screws.
  • a further flange 35 may be provided on the plug 33, for example, to limit the depth of penetration of the plug shank 34 into the hole 32, although it will be appreciated that a number of other ways of thus locating the plug 33 could be used.
  • bleed communication between the working chamber and the fluid inlet takes the form of a passageway formed integrally within the casing, other forms of bleed communication could be provided.
  • a pressure line for example, could be coupled between the discharge arrangement and a point in the fluid inlet to provide fluid communication between the working chamber and the fluid inlet.
  • FIGS 4, 5, 6 and 7, showing the four embodiments of a discharge arrangement according to the invention each show only one opening for providing permanently open fluid communication between the working chamber and the passageway. It will be understood, however, that any number of such openings could be provided in the casing and the openings may be of different sizes. Indeed, giving consideration to production line operations in the manufacture of compressors according to this invention, it may be desirable to provide a number of such openings in each unit as a standard operation. The desired rate of fluid bleed from each standard compressor off the production line could thus be determined by plugging off a suitably selected combination of openings in the discharge arrangement.
  • openings in the casing are conveniently drilled from the outside of the casing, rendering the closure means externally accessible, other means for providing such openings could be used. Openings could be drilled into the casing from the inside of the working chamber, for example, or such openings could be provided by holes formed in the casing as an integral part of the casting.
  • the discharge arrangement prefferably rendered as tamper-proof as possible so that the fixed rate of fluid bleed determined for a particular compressor during manufacture cannot easily be adjusted subsequently.
  • a major advantage of this invention is that an extensive range of fluid output capacities is available from compressors built according to the invention at a minimal cost in terms of deviating from present manufacturing production and that the invention is extremely sympathetic to standardisation of parts and production line operations.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary-Type Compressors (AREA)
EP82301011A 1981-03-04 1982-02-26 Schraubenverdichter Withdrawn EP0060639A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB8106754 1981-03-04
GB8106754A GB2093915A (en) 1981-03-04 1981-03-04 Rotary compressors

Publications (1)

Publication Number Publication Date
EP0060639A1 true EP0060639A1 (de) 1982-09-22

Family

ID=10520127

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82301011A Withdrawn EP0060639A1 (de) 1981-03-04 1982-02-26 Schraubenverdichter

Country Status (5)

Country Link
EP (1) EP0060639A1 (de)
JP (1) JPS57148094A (de)
AU (1) AU8097582A (de)
GB (1) GB2093915A (de)
ZA (1) ZA821245B (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1986006798A1 (en) * 1985-05-09 1986-11-20 Svenska Rotor Maskiner Ab Refrigeration plant and rotary positive displacement machine

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE439042B (sv) * 1983-07-20 1985-05-28 Imo Ab Skruvpump med regleranordning
GB2212605B (en) * 1987-11-17 1991-05-29 Cico Chimney Linings Limited Lining chimneys
US4925372A (en) * 1989-04-07 1990-05-15 Vickers, Incorporated Power transmission

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB420501A (en) * 1933-09-29 1934-12-03 Sulzer Ag Improvements in or relating to rotary compressors
US2623469A (en) * 1948-07-23 1952-12-30 Gray Company Inc Gear pump
FR1303685A (fr) * 1961-08-23 1962-09-14 Studia Technica Ets Machine rotative
GB1576230A (en) * 1976-09-15 1980-10-01 Aerzener Maschf Gmbh Meshing-screw compressor

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB420501A (en) * 1933-09-29 1934-12-03 Sulzer Ag Improvements in or relating to rotary compressors
US2623469A (en) * 1948-07-23 1952-12-30 Gray Company Inc Gear pump
FR1303685A (fr) * 1961-08-23 1962-09-14 Studia Technica Ets Machine rotative
GB1576230A (en) * 1976-09-15 1980-10-01 Aerzener Maschf Gmbh Meshing-screw compressor

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1986006798A1 (en) * 1985-05-09 1986-11-20 Svenska Rotor Maskiner Ab Refrigeration plant and rotary positive displacement machine
US4748831A (en) * 1985-05-09 1988-06-07 Svenska Rotor Maskiner Ab Refrigeration plant and rotary positive displacement machine

Also Published As

Publication number Publication date
GB2093915A (en) 1982-09-08
AU8097582A (en) 1982-09-09
JPS57148094A (en) 1982-09-13
ZA821245B (en) 1983-01-26

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PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

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Inventor name: MORRIS, SIDNEY JOHN