EP0320684A2 - Dispositif de contrôle pour compresseurs rotatifs à air - Google Patents

Dispositif de contrôle pour compresseurs rotatifs à air Download PDF

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Publication number
EP0320684A2
EP0320684A2 EP88119793A EP88119793A EP0320684A2 EP 0320684 A2 EP0320684 A2 EP 0320684A2 EP 88119793 A EP88119793 A EP 88119793A EP 88119793 A EP88119793 A EP 88119793A EP 0320684 A2 EP0320684 A2 EP 0320684A2
Authority
EP
European Patent Office
Prior art keywords
valve
compressor
oil
intake
chamber
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
EP88119793A
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German (de)
English (en)
Other versions
EP0320684A3 (en
EP0320684B1 (fr
Inventor
Adolfo Boldrini
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.)
Ing Enea Mattei SpA
Original Assignee
Ing Enea Mattei SpA
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 Ing Enea Mattei SpA filed Critical Ing Enea Mattei SpA
Priority to AT88119793T priority Critical patent/ATE94619T1/de
Publication of EP0320684A2 publication Critical patent/EP0320684A2/fr
Publication of EP0320684A3 publication Critical patent/EP0320684A3/en
Application granted granted Critical
Publication of EP0320684B1 publication Critical patent/EP0320684B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04C28/24—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

Definitions

  • This invention refers to oil-sealed rotary air compressors, and more particularly to a control apparatus able to switch the working of the compressor from an operative condition having modulated adjustment of the delivery to an intermittent full-­load and idle working condition, while at the same time venting the pressure inside the compressor to reduce power consumption.
  • Oil-sealed rotary air compressors comprising an intake-valve control system, in which a pressure sensing switch senses the delivery pressure of the compressed air and controls the transition from a full-load working condition, in which the compressor operates uninterruptedly, automatically modulating the delivery by means of a suitable servovalve, to an idle-working condition in which, for want of air demand or owing to limited air demand which are satisfied directly by the compressed air stored in tank, the compressor is made to idle, at the same time venting its internal pressure.
  • the control of the intake valve is effected by means of a control piston actuated by the pressure of the oil coming from the compression chamber.
  • the pressure of the operative fluid is controlled by a servovalve, through which the oil reaches the control piston of the intake valve.
  • a small variation of the pressure in the oil chamber causes the pressure on the control piston of the intake valve to assume the necessary values for overcoming the force of the spring restraining the piston, so that it can complete its full stroke.
  • the oil is delivered directly to the intake-valve control piston in such a way that the pressure acting on it is the same pressure existing in the oil chamber.
  • the compressor can decompress until the internal pressure assumes the minimum value necessary for keeping the intake valve closed. At this value the intake valve will compensate the air which is released, so holding the internal pressure constant, the latter being needed also for the circulation of the lubrication oil for the compressor.
  • An object of this invention is to provide a new control apparatus allowing the direct passage of the oil from the compression chamber to the intake-valve control cylinder, and which at the same time releases the pressure of the air inside the compressor, said apparatus enabling to control the closing of the intake-valve in complete autonomy from the opening of the servovalve for the modulated working of the compressor and therefore from the need to close the air-eelivery valve and to reach the maximum set pressure of the pressure valve as required instead with previously known control apparatus.
  • control pressure switch normally present in these types of apparatus can be adjusted for any operative value of the required pressure and idle working of the compressor can occur without the pressure of the air inside the compression chamber needing to attain the maximum set value of the above-mentioned servovalve. In this way an apparatus of simple design and which is able to offer a significant power saving is obtained.
  • an apparatus for controlling a rotary air compressor having an intake valve operatively connected to the piston of a control cylinder connected to the oil chamber or oil sump of the compressor via a servovalve operated by said pressurized oil, and in which an idling valve to switch the compressor into an idle working condition has been provided to connect directly the control cylinder of the intake-valve to the oil chamber, in which the control side of the aforesaid idling valve is operatively connected to the compressor air separator via a solenoid valve controlled by a pressure switch that senses the air pressure delivered by the compressor, and respectively is connected to the outside, characterized by the fact that the intake-valve control cylinder can be directly connected to the oil chamber via a separate path comprising a normally closed idling valve having a closing element subjected to the pressure of the oil in the compression chamber, said closing element being mechanically connected to the piston of a control cylinder actuable in opposition to the oil pressure acting on said closing element, by the air pressure
  • FIG. 1 shows the diagram of the control apparatus for an oil-sealed rotary air compressor, per sè known, and of which a few essential working parts are presented in figures purely for the purposes of this invention.
  • the compressor 10 comprises a rotor chamber 11, connected to an oil chamber or sump 12, and respectively with a separator or chamber 13 for separating the compressed air from the oil entrained in it; the separator chamber 13 in its turn communicates with an outlet or air discharge duct 14 through a minimum pressure valve 15, whose closing element 16 is pushed in a closed condition against a sealing seat by a spring 17.
  • Reference number 18 in figure 1 indicates the overall assembly of a compressor intake valve through which the rotor chamber 11 can be connected to the outside by means of suitable air passages, not shown, in a fairly conventional way.
  • the intake valve 18 can be of any type and for this purpose can equally be both of the open and closed type.
  • the intake valve 18 comprises a closing element 19 which is pushed to close the air intake 20 by a hydraulic cylinder 21 operated by the pressurized oil in the compressor oil chamber 12.
  • the closing element 19 is mechanically connected to a control piston 21′ pushed in a direction in which the valve opens by a spring 22 acting against the pressurized oil fed on the opposite side through a duct 23; the duct 23 is connectable to the compressor oil chamber 12 through a first path comprising a servovalve 24, and then through a second branched-off path comprising an idling valve 25 for switching the compressor into an idle working condition as explained below.
  • the oil feeding duct 23 for feeding the oil to the intake-valve control cylinder 21 is connected also to the air intake chamber 26 of the compressor through a duct 26′ comprising a restricted orifice 27.
  • the servovalve 24 is connected on one side to the intake-valve control cylinder 21 through the duct 23, as already stated, and on the other it is connected to the oil chamber 12 through a duct 28; the servovalve 24 comprises a closing element 29 for modulating the oil pressure to the cylinder of the intake valve 18, this closing element being caused to open by the pressure of the oil, in opposition to the action of a thrust spring 30.
  • the pressurized oil in the oil chamber 12 can be fed directly to the intake-valve control cylinder 21 through the idling valve 25 without interfering with the function of the servovalve 24; in this connection, as shown in the diagram of figure 1, the idling valve 25 comprises a chamber 31 connected directly to the oil chamber 12 or for example through the duct 32 branched-off from the duct 28. In the chamber 31 there is a closing element 33 pushed by the oil pressure to close against a seat formed at the end of an axial hole or passage 34 which opens into the chamber 31, and is also connected to the duct 23 through an annular chamber 35 appropriately provided in the servovalve 24, around the closing element 29.
  • the closing element 33 of the idling valve is connected by a rod 36 to a piston 37 of a control cylinder 38 whose working side is connected via a duct 39 and a solenoid valve 40, to the separator chamber 13.
  • the duct 39 or the working side of cylindre 38 is connected also to the atomosphere through openings 41 in the cylinder chamber 38, which could be fitted with a silencing filter.
  • the solenoid valve 40 is in its turn controlled by a pressure switch 42 activated by the pressure of the compressed air discharged by the compressor; this pressure switch is therefore operatively connected with the delivery 14 through the duct 43.
  • the compressor governs itself by modulating the delivery through control of the intake valve effected by means of the servovalve 24.
  • the solenoid valve 40 is closed and prevent the supply of pressurized air to the idling valve 25; the latter in its turn closes off the direct passage 32, 34 of the pressurized oil from the compressor chamber 12 to the control piston 21′ of the intake valve 18. Accordingly, only the servovalve 24 can deliver oil to the intake valve control cylinder 21, modulating the air pressure.
  • a direct connection is established between the oil chamber 12 and the intake valve 18 for any value of the pressure inside the compressor.
  • the intake value 18 will remain closed until the air pressure inside the compressor has fallen to the minimum value necessary for holding the valve completely closed, after which the suction of air will compensate the quantity of air released or vented, thereby maintaining the internal pressure of the compressor at the above-mentioned value.
  • the pressure at the outlet 14 has fallen, through the demand for air, at the value at which the pressure switch 42 will close the solenoid valve 40, the flow of air to the control piston 37 of the idling valve 25 will be stopped and the piston's face will once again be subject to atmospheric pressure returning through the venting holes 41 in the cylinder.
  • FIG. 2 shows a preferred embodiment of an idling valve as described above, forming part of the same assembly comprising the intake valve and the servovalve.
  • the idling valve comprises a screw plug 45 having a tubular extension 46 protruding into a cylindrical hole 48 of the body 10, having a diameter larger than the outer diameter of the extension 46; the fore end portion 47 of extension 46 has a wider diameter, than the rear intermediate portion, equal to that of hole 48, to form a seal, so that the upper part of hole 48, forms annular-shaped passage 50, communicating with one side of the control cylinder of the intake valve 18 through a passage 52.
  • the piston 51 of control valve actuates the closing element 53 of the intake valve overcoming the force of a return spring 54 disposed between the cup-shaped piston 51 and the enlarged portion of a bush member 55, in order to push the closing element 53 normally in a closed condition against a ring-­shaped sealing seat 56.
  • a stem 57 having a mushroom head 58 at one end which forms a seal against a conical seating 59 provided at the end portion 47 of the cylindrical body 46, in respect to the pressurized oil coming from the oil chamber of the compressor, through a duct 60 which feeds the oil both to the servovalve 24 and the idling valve 25, passing through the annular shaped chamber 61 provided by a reduced portion of a sliding member at the bottom of the valve 24; in particular, the chamber or space formed at the bottom of the valve housing or bore 48, into which the duct 60 opens, when the closing element 58 is in open condition, communicates with the annular shaped passage 50 in the axial bore 48 of the cylindrical body 46 at a location where the stem member 57 has a reduced diameter, defining an annular space having radial holes 46′ in the cylindrical body 46 as shown.
  • the head portion of the screw plug 45 is hollow and comprises a cylindrical hole 62 defining a control cylinder within which slides a piston 63 connected to stem 57.
  • the cylinder 62 on the side opposite to stem 57 is connected to the compressor downstream the filtering separator, through the duct 35 and the solenoid valve 40 controlled by the pressure switch 42 which senses the delivery pressure, in the way previously described.
  • the delivery side of the servovalve 24 is in communication with the annular shaped duct 50 through a hole 64 in the body 10 and at the same time, on the opposite side, it communicates with the compressor intake chamber through an annular groove 65 in the piston of valve 24 and a restricted orifice 66.
  • the pressurized oil from the oil chamber 12 will find an open passage leading to the annular duct 50 and from this it will reach the piston 51 of the intake valve 18 so completely closing the valve.
  • the pressure switch 42 again closes the solenoid valve 40, and with the thrust of the working piston 63 being released, the pressure of the oil will automatically re-close the element 58.
  • the pressure acting on the intake-valve piston will be released through the orifice 66 towards the compressor intake chamber, the intake valve will re-open and the compressor will revert to full-load working.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Rotary Pumps (AREA)
EP88119793A 1987-12-15 1988-11-28 Dispositif de contrôle pour compresseurs rotatifs à air Expired - Lifetime EP0320684B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88119793T ATE94619T1 (de) 1987-12-15 1988-11-28 Regelungseinrichtung fuer drehkolbenluftverdichter.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT2300987 1987-12-15
IT23009/87A IT1223469B (it) 1987-12-15 1987-12-15 Apparecchiatura per il controllo di un compressore d'aria rotativo

Publications (3)

Publication Number Publication Date
EP0320684A2 true EP0320684A2 (fr) 1989-06-21
EP0320684A3 EP0320684A3 (en) 1990-01-10
EP0320684B1 EP0320684B1 (fr) 1993-09-15

Family

ID=11202834

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88119793A Expired - Lifetime EP0320684B1 (fr) 1987-12-15 1988-11-28 Dispositif de contrôle pour compresseurs rotatifs à air

Country Status (5)

Country Link
EP (1) EP0320684B1 (fr)
AT (1) ATE94619T1 (fr)
DE (1) DE3884162T2 (fr)
ES (1) ES2046276T3 (fr)
IT (1) IT1223469B (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT401551B (de) * 1994-03-30 1996-10-25 Hoerbiger Ventilwerke Ag Vorrichtung zur druckabsenkung eines verdichters

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2722395A (en) * 1951-05-28 1955-11-01 Alfred Bullows & Sons Ltd Inlet control valves for air or other gas compression or vacuum pumps
DE2516582A1 (de) * 1974-04-17 1975-10-30 Hydrovane Compressor Kreiskolbenkompressor
GB1486941A (en) * 1975-01-27 1977-09-28 Hydrovane Compressor Compressors of sliding vane eccentric rotor type
FR2392258A1 (fr) * 1977-05-25 1978-12-22 Hydrovane Compressor Compresseur rotatif

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2722395A (en) * 1951-05-28 1955-11-01 Alfred Bullows & Sons Ltd Inlet control valves for air or other gas compression or vacuum pumps
DE2516582A1 (de) * 1974-04-17 1975-10-30 Hydrovane Compressor Kreiskolbenkompressor
GB1486941A (en) * 1975-01-27 1977-09-28 Hydrovane Compressor Compressors of sliding vane eccentric rotor type
FR2392258A1 (fr) * 1977-05-25 1978-12-22 Hydrovane Compressor Compresseur rotatif

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT401551B (de) * 1994-03-30 1996-10-25 Hoerbiger Ventilwerke Ag Vorrichtung zur druckabsenkung eines verdichters

Also Published As

Publication number Publication date
IT8723009A0 (it) 1987-12-15
EP0320684A3 (en) 1990-01-10
ES2046276T3 (es) 1994-02-01
DE3884162D1 (de) 1993-10-21
EP0320684B1 (fr) 1993-09-15
IT1223469B (it) 1990-09-19
ATE94619T1 (de) 1993-10-15
DE3884162T2 (de) 1994-05-05

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