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Publication numberUS3367562 A
Publication typeGrant
Publication dateFeb 6, 1968
Filing dateJun 23, 1966
Priority dateJun 23, 1966
Also published asDE1628144A1, DE1628144B2, DE1628144C3
Publication numberUS 3367562 A, US 3367562A, US-A-3367562, US3367562 A, US3367562A
InventorsPersson Jan Edvard, Olofsson Hans Kristofer
Original AssigneeAtlas Copco Ab
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Means for unloading and controlling compressor units
US 3367562 A
Abstract  available in
Images(3)
Previous page
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Claims  available in
Description  (OCR text may contain errors)

Feb. 6, 1968 1 E, PERSSON ET AL 3,367,562

MEANS FOR UNLOADING AND CONTROLLING COMPRESSOR UNITS 75 fgl I Feb. 6, 1968 J, E, PERSSON ET AL 3,367,562

MEANS FOR UNLOADING AND CONTROLLING COMPRESSOR UNITS Filed June 23, 1966 3 Sheets-Sheet 2 IV TOR. Jn fzfara] rssnn 75 Fig. 2 l

Feb. 6, 1968 1. E. PERssoN ET AL 3,367,562

MEANS FOR UNLOADING AND CONTROLLING COMPRESSOR UNITS Filed June 23, 1966 5 Sheets-Sheet 5 77 INVENTOR Ja h J1/a nl arss ow United States Patent O 3,367,562 MEANS FOR UNLOADING AND CONTROLLING COMPRESSOR UNITS Jan Edvard Persson, Ektorp, and Hans Kristofer Olofsson, Segeltorp, Sweden, assigner-s to Atlas Copco Aktiebolag, Nacka, Sweden, a corporation of Swed'en Filed June 23, 1966, Ser. No. 564,474 12 Claims. (Cl. 230-24) This invention relates to compressor units for supplying and maintaining a compressed uid under predetermined super atmospheric pressure and the invention is particularly related to means for unloading and controlling such a compressor unit. One object of the invention is to provide a simple and reliable unloading and control device which may be used for portable as Well as stationary compressors. A further object of the invention is to provide an unloading device which may be used for single stage compressors but which is particularly suitable for two or multiple stage compressors. A still further object is to provide a device in which spring means only are relied upon for maintaining the compressor in unloaded condition. For the above and other purposes we provide a compressor unit for supplying and maintaining a compressed working huid under predetermined super atmospheric pressure and comprising a compressor, a working iiuid intake conduit in flow communication with said compressor, a throttle valve in said intake conduit movable from a first throttle position to a second fully open position and vice versa, a compressed working tluid receiver, a comintercooler 9 from which a conduit 10 leads to the intake of the high pressure compressor 3. From the high pressure compressor 3 the compressed air flows through a delivery conduit 11, 12 to an after cooler 13 and an air receiver 14. The delivery conduit contains a check valve 15 which in closed position separates the conduit portions 11 and 12, and which prevents back ow from the air receiver 14 when the compressors 2 and 3 are stopped or unloaded. 16 is a safety valve communicating with the delivery -conduit before the check valve 15. From the delivery conduit 11 a blow oif conduit 17 leads to a chamber 18 communicating with a cooler and silencer 19 through a conduit 20. A conduit 21 connects the silencer and cooler 19 to the intake conduit 4, which may be provided with an air intake filter and silencer in conventional manner. A valve member 22 controls the communication between the conduit 17 and the chamber 18.

The valve member 22 and an operating member 23 for the throttle valve 6 are provided on a rod 24 which is connected to a piston 25 operating against a membrane 26 and movable in a cylinder 27 which is separated by said membrane in a irst chamber 23 and a second chamber 29. The membrane 26 is preferably a rolling membrane, which is not xed to the piston 25. The tirst chamber 28 communicates through a restricted pipe or bore 30 with the intake conduit portion 5 and furthermore through a pipe or bore 31 with an auxiliary valve device 32. A conpressed working fluid delivery conduit leading from the compressor to said receiver, a check valve in said delivery conduit, a vent passage communicating with the delivery conduit between the compressor and said check valve, a vent valve in said vent passage movable from a first open position to a secon-d closed position and vice versa, spring means arranged for moving said throttle valve and said vent valve to said rst positions for unloading the compressor, and workin g fluid pressure responsible means arranged for moving the throttle valve and the vent valve to said second position for loading the compressor.

In the enclosed drawings three embodiments of two stages compression compressor units according to the invention are illustrated diagrammatically by way of eX- ample. FIG. 1 is a diagrammatic view of a two stage compressor unit according to the invention intended for portable use. FIG. 2 is a similar diagrammatic View illustrating a two stage compressor unit for stationary purposes. FIG. 3 illustrates a modification of FIG. 2.

In FIG. 1 a power transmission casing 1 is illustrated which carries a low pressure compressor 2 and a high pressure compressor 3 which may be screw compressors driven from a common shaft (not illustrated) in the power transmission casing 1. 4 and 5 are different portions of an air intake conduit of the low pressure compressor 2. Naturally the intake conduit may instead `be connected to a source of gas if the compressor is operating on gas, but the following description refers to air only, since the necessary modifications for handling gas would be obvious to any one skilled in the art. The air intake conduit portions 4 and 5 are separated by a throttle valve 6 which may take a iirst throttle position, as illustrated in FIG. 1 in which position the valve permits a limited air flow from the intake conduit portion 4 to the intake conduit portion 5 over the edges of the throttle valve member or through a suitable restricted port 7 in the throttle valve member. The throttle valve member may also take a fully open position in which air or other gas may flow freely from the air intake conduit portion 4 to the portion 5. From the low pressure compressor 2 compressed air or other fluid flows through a conduit 8 to an duit 70 connects the second cylinder chamber 29 with the auxiliary valve device 32.

A spring 33 is provided in the cylinder 27 and gives the piston 25 and membrane 26 a spring bias in such a direction that the spring tends to close the throttle valve 6 and to open the blow-ofir valve 22.

The auxiliary valve 32 includes a first space 34, a second space 3S and an intermediate space 36 and, furthermore, a dou-ble headed valve member 37 having a rst head 38 and a second head 39 connected by a stem. A spring 40 disposed in the valve device 32 acts on a membrane 41 to bring the valve member 37 to the position in which the valve head 39 separates the second space 35 from the intermediate space 36. A second spring 42 acts in the opposite direction on a membrane 43 to move the valve member 37 to a position in which the valve head 38 interrupts communication between the intermediate space 36 and the first space 34. The tension of the spring 42 is determined by a piston 44 which has two distinct positions as follows: When there is no pressure supplied through an oil inlet 45 from an oil pipe 46 the piston 44 is in the lower position which is as illustrated in FIG. l and the spring 42 then has low tension. The spring 40 then overcomes the spring 42 and keeps the valve member 37 in the lower position as illustrated in FIG. 1. When a suitable oil pressure is supplied through inlet 45 piston 44 moves to the upper position defined by lugs 87. Spring 42 then has enough tension to overcome spring 4) and to push valve member 37 to its upper position provided chamber 74 is under atmospheric pressure. Piston 44 is preferably sealed by a rolling membrane 48 which separates a chamber 47 from a space 49 in which the spring 42 is provided. Said space is preferably connected to the atmosphere through an aperture 50.

The second space 35 in the auxiliary valve device 32 is connected through a conduit 51 to a selector valve 52 which contains a valve chamber 53 in which a flexible rubber valve member 54 is movable `from the illustrated position in which it closes the inlet opening 55 of a conduit 56 to a position in which the valve closes an opening 57 of a conduit 58 which connects the valve chamber 53 with the intake conduit 4. The conduit 56 connects the valve chamber 53 with the conduit 8 from the low pressure compressor to the intercooler. The conduit 51 is connected to the valve chamber 53 through an opening 59 which is not aiiected by the movements of the valve member 54 and is therefore constantly in communication with the valve chamber 53.

The oil pipe 46 is connected to a control valve 60 which is illustrated diagrammatically and is capable of taking two positions a and b. The valve 60 is connected to the pipe 46 through a pipe 61 and to a source of pressure oil such as the lubricating oil pump of the compressor through a pipe 62, and, furthermore, through a pipe 63 to a not illustrated oil drain chamber. The valve 60 is manipulated by means of a push button 64 provided on a stem 65 carrying a piston 66 movable in a cylinder 67 which through 68 is connected to the oil pipe 46, and the valve member 60 is biased in opposite direction to the pushbutton 64 by a spring 69. 71 is a conduit from the receiver to a conventional pressure control valve 72, which at an air pressure for which the valve is set supplies compressed air from the receiver through a conduit 73 to a space 74 in the auxiliary valve device 32. When the receiver pressure falls below a certain value the valve 72 vents the conduit 73 to the atmosphere.

The above described compressor unloading and control apparatus operates in the following manner: When the compressor is at rest no oil pressure exists in the oil pipe 62 and control valve 60 is in the position a, in which the cylinder 67 and the oil inlet 45 are connected to the oil drain pipe 63 through the pipes 46, 68 and 61. The auxiliary valve device 32 is in the position illustrated in FIG. 1, since the tension of spring 40 is higher than the tension of spring 42. The throttle valve operating rod 24 is also in the position illustrated in FIG. 1 due to the action of the spring 33 on the piston 25 and, consequently, throttle valve 6 is in the throttle position in which the air admission from the air intake conduit 4 to the air intake conduit 5 is throttled or restricted as by the port 7. Furthermore, the valve member 22 is in open position so that delivery conduit 11 is connected to the atmosphere. The valve member 54 is in neutral position.

Now, if the compressor motor is started and the compressor starts to rotate the oil pump of the compressor connected to the pipe 62 supplies pressure oil to the pipe 62. As long as the valve 60 is in the illustrated position the oil in the pipe 62 is blocked and cannot enter pipes 61, 46, 68. Since the throttle valve 6 is in throttling position the compressor very soon produces vacuum in the inlet conduit 5 and said vacuum is distributed through the restricted pipe or bore 30 to the iirst chamber 28 in the cylinder 27 and further through the pipe 31, the first space 34 in the auxilitary valve 32, the intermediate space 36 and the pipe 70 to the second chamber 29 of the cylinder 27. The vacuum in the intake conduit 5 consequently acts on both sides of the membrane 26 in the cylinder 27, so that the spring 33 continues to keep the operating rod 24 in the illustrated position while the compressor is running unloaded. Vacuum is also created in the inter cooler 9 and consequently in the conduit 56 and the rubber valve 54 is therefore moved to the position illustrated in FIG. 1, in which it closes the opening 55 and permits atmospheric air to enter through the pipe 58 to the valve chamber 53 and the pipe 51 leading to the auxiliary valve device 32. The air circulated through the compressor is passed from the delivery conduit 11 through the blow off conduit 17 and the chamber 18 to a cooler and silencer 19 from which the air is returned through the conduit 21 to the air intake conduit 4 so that substantially no external air is drawn into the compressor.

Now, when it is desired to load the compressor, the operator pushes the button 64 and thereby moves the valve 60 against the spring 69 to the position b. Pressure oil is then admitted from the pipe 62 through pipe 61 to pipes 46 and 68 and the oil entering through the inlet 45 to the chamber 47 moves the membrane 43 and piston 44 to contact with lugs 87 thereby increasing the tension of the spring 42 so that the spring 42 can move the valve member 37 from the illustrated position to a position in which the first valve head 38 closes the communication between the iirst space 34 and the intermediate space 36. Simultaneously pressure oil through the pipe 68 enters the cylinder 67 and acts on the piston 66 so that the pushbutton and the valve 60 against action of the spring 69 is held in the position b, even when the operator has finished to press the `button 64. The movement of the valve member 37 closes the communication between the second chamber 29 and the vacuum in the compressor intake conduit 5 and instead connects the second chamber 29 through intermediate space 36, second space 35 in the valve device 32, conduit 51 and chamber 53 in the selector valve 52, through conduit 58 to the air intake conduit 4 in which atmospheric pressure prevails. Since atmospheric pressure enters the second chamber 29 and intake vacuum is in the first chamber 28, the piston 25 and membrane 26 move the operating rod 24 against the action of spring 33, so that the blow-olf valve 22 is closed and the throttle valve 6 is moved to open position. Due to the restricted area of pipe 30 it takes some time before vacuum in 28 is raised to the atmospheric pressure. Pressure starts to build up in the intercooler and the conduit 8 and when said pressure has increased above atmospheric pressure the valve 54 no longer remains in the illustrated position since pressure above atmospheric in 56 moves the valve 54 towards the opening 57 which is now closed so that intercooler pressure enters chamber 53 and pipe 51 and the second space 3S in auxiliary valve device 32. Since the auxiliary valve member 37 is in upper position the inter cooler pressure also enters intermediate space 36, pipe 70 and second chamber 29 in the cylinder 27 in which inter cooler pressure acts to keep the valve control rod in open throttle position and the valve 22 in closed position against the spring 33 and the rising pressure in 17 and in spite of the fact that vacuum in the intake conduit 5 is replaced by atmospheric pressure as soon as the throttle valve 6 opens fully. The compressor unit consequently continues to run loaded and the throttle valve 6 remains in open position and the valve 22 in closed position.

The air receiver 14 is connected through the conduit or pipe 71 to the conventional pressure control or pressure regulator valve 72 which, when the air pressure in the receiver 14 reaches a predetermined maximum value supplies regulating air through conduit 73 to chamber 74 in the auxiliary valve device 32. When pressure air is admitted to the chamber 74 said pressure air together with the spring 40 move the valve member 37 to the position illustrated in FIG. 1 in which the valve head 39 closes the communication Ibetween the second space 35 and the intermed-iate space 36. The movement of the valve member 3-7 opens communication between the pipe 31 through first space 34, intermediate space 36 and pipe 70 to the second cham-ber 29 in the cylinder 27. Intake air pressure consequently prevails both in chamber 29 and chamber 28 and the spring 33 together with the high air pressure in blow-ofi pipe 17 opens the valve 22 and closes the throttle valve 6 so that they take again the position illustrated in FIG. 1 thereby unloading the compressor. As soon as the throttle valve 6 is closed vacuum again builds up in the air intake conduit 5 which vacuum is distributed to iirst and second cylinder chambers 28 and 29 so that the spring 33 can keep the throttle valve in throttling position and the blow-off valve 22 open. Since vacuum is produced in the inter cooler also pressure is reduced in the conduit 56 and moves valve 54 over to the position illustrated in FIG. 1 so that the pressure in the second space 35 is reduced to atmospheric pressure via opening 59, valve chamber 53, conduit 58 and the air intake conduit 4. The compressor then continues to run unloaded and the valve 60 remains in the position b since oil pressure still keeps the valve 60 in the position [1 by actuating the piston 66.

Now, if the air pressure in the receiver 14 due to air consumption of a consumer connected to the discharge conduit 75 should sink below the low value for which the regulating valve 72 is set, then the regulating air pressure in the pipe 731 is vented to atmosphere in the regulating valve 72 in conventional manner so that air pressure is removed from the chamber 74 and consequently the tension of the spring 42 moves the valve member 37 to the upper position in which the iirst valve head 38 closes the communication between the first space 34 and the intermediate space 36 and the second valve head 39 opens the communication between the intermediate space 36 and the second space 3S. Atmospheric pressure through conduit 58, selector valve chamber 53, pipe 51, second space 35, intermediate space 36 and pipe 70 then reaches into the second cylinder chamber 29 and acts against the vacuum in the first cylinder chamber 28 and the spring 33 to move the operating member 23 and the operating rod 24 to the left in FIG. 1 thereby open-ing throttle valve 6 and closing blow-off valve 22. The compressor unit is now loaded again and the operation continues as above described.

When the compressor motor is stopped the compressor returns to unloaded condition and since oil pressure then disappears in the oil pipe 62 spring 69 moves the valve 60 to the position a, in which oil is drained from cylinder `67 and chamber 47 and the pushbutton 64 takes again the position illustrated in FIG. 1.

The above described regulating device is only an example and may also be used for single stage compressors in which case, however, the pipe 56 is connected to the delivery conduit 11 instead of to the conduit 8 to the inter cooler.

The above described device may also be modified as indicated in chain-dotted lines in FIG. 1 by replacing the conduit 58 by a conduit 88 or 88, 89 which connects opening 57 to the delivery conduit portion 11 or the receiver 14, respectively. This arrangement gives the same general operation but a smaller area on the cylinder 27 and membrane 26 which is of particular advantage in large compressors. As above described the membrane 26 is first operated by vacuum and then by delivery pressure or receiver pressure.

In the embodiment of FIG. 2 which illustrates a stationary compressor unit with electric control all parts equivalent to parts in FIG. 1 have been indicated by the same reference numerals as in FIG. 1 and are therefore not described again. The difference between the arrangements in FIG. 2 and FIG. l is that the control valve 60 in FIG. 1 has been replaced by an electromagnetic valve 76 which is interposed between the pressure oil pipe 62 Aand the oil drain pipe 63 and the oil pipe 46 leading to the auxiliary valve device 32. The solenoid controlled valve 76 can take two positions a and b and in the position a the oil pipe 46 is connected to the drain pipe 63. The compressor may be started by closing a switch 80 for the motor contactors 81 connected between the electric leads 82, 83. A time lag relay 84 having a switch 85 is connected in parallel with the motor contactor 81 and switch 8S is closed with suitable delay after the switch 80 has been closed. A pressure switch 77 is provided on the receiver and is closed as soon as receiver pressure is below a certain minimum value and is opened when receiver pressure rises above a certain maximum pressure. The pressure switch is connected in a circuit 78 including a solenoid 79 for the valve 76. When solenoid 79 is deenergized valve 76 is moved by a spring 86 to position a in which chamber 47 through 46 is drained and spring 40 moves valve member 37 to the position illustrated in FIG. 2 in which spring 33 keeps operating rod 24 to the right and throttle valve 6 closed and blow-Off valve 22 open.

The operation of the compressor unit in FIG. 2 is as follows:

When the motor and compressor is at rest the valves 6, 15, 22, 37, 48 and 76 and the switches are -in the illustrated positions and if no or low air :pressure is in the receiver, the switch 77 is closed and solenoid 79 deenergized. The compressor is in unloaded condition. Now, if the motor is started by closing the switch 80 the motor contactors 81 are closed and the motor starts to rotate the compressor. Oil pressure from the oil pump immediately is supplied to pipe 62 which -is closed. The compressor immediately produces vacuum in 5, 30, 31, 34, 36, 70, 28, 29 and 9 and selector valve 54 takes the illustrated position. After a predetermined time delay which allows the motor and compressor to reach full speed time lag relay 84 closes switch 85 so that solenoid 79 is energized and moves valve 716 to position b thereby supplying pressure oil to chamber 47 and moving 44 to contact lug 87, moving valve member 37 so that 38 interrupts communication between 31 and 70 and 3-9 admits atmospheric air to 29 so that throttle valve 6 is opened anl blow-olf valve 22 is closed as described in connection with FIG. 1. The compressor is now loaded and operates as in FIG. 1.

When maximum pressure is reached in the receiver 14 pressure switch 77 is opened and solenoid 79 deenergized and valve 76 is moved to unloading position a by spring In the embodiment of FIG. 3 which is rather a modication of FIG. 2 the auxiliary valve device 32 has been replaced by a valve 1176 operated by a solenoid 179 and a spring 186. The valve 176 is connected to the chamber 28 by a pipe 131 and to the selector valve 52 by a conduit 151. When the solenoid 179 is deenergized valve 176 takes the unloading position a in which chamber 29 through 70, 176, 131 communicates with chamber 28 and the intake conduit vacuum. When maximum pressure is reached in receiver 14 pressure switch 77 breaks its contacts and causes solenoid 179 to be deenergized. When pressure in the receiver has dropped to a predetermined value pressure switch 77 closes its contacts and solenoid 179 is energized whereby valve 1-76 is moved to position b'and the compressor loaded in the same manner as described in connection with FIG. 2.

The embodiments of the invention above described and illustrated on the drawings are only to be considered as examples and may be modified in various ways Within the scope of the claims.

What we claim is 1. A compressor unit for supplying and maintaining a compressed working fluid under predetermined superatmospheric pressure and comprising -a compressor, a working Huid intake conduit in flow communication with said compressor, a throttle valve in said intake conduit movable from a first throttle position to a second fully open position and vice versa, a compressed Working uid receiver, a compressed working fluid delivery conduit leading from the compressor to said receiver, a check valve in said delivery conduit, a vent passage communicating with the delivery conduit between the compressor and said check valve, a vent valve in said vent passage movable from a rst open position to a second closed position and vice versa, spring means arranged for moving said throttle valve and said vent valve to said rst positions for unloading the compressor, and working liuid pressure responsible means arranged for moving the throttle valve and the vent valve to said second positions for loading the compressor.

2. A compressor unit according to claim 1, in which the working fluid pressure responsible means consists of a control cylinder, a control piston movable in said cylinder, a member coupling said control piston to the throttle Valve and to the vent valve, first and second working chambers in the cylinder separated by the piston, working fluid conduit means arranged for interconnecting said chambers for unloading of the compressor and for separating the chambers and subjecting them to a difference in working fluid pressure for loading of the compressor.

3. A compressor unit according to claim 2, in which first and second working uid conduit means are provided for connecting said rst and second chambers to vacuum in the intake conduit between the throttle valve and the compressor during unloading of the compressor and in which said first working fiuid conduit means is arranged for connecting said first chamber to atmosphere upon loading of the compressor, and in which a third conduit means is arranged for supplying compressed working fiuid to said second chamber for maintaining the compressor in loaded condition after loading of the compressor.

4. A compressor unit according to claim 3, in which the compressor has at least two compression stages, an intercooler between said two stages, and in which said third conduit means connects the second chamber to the atmosphere or the intercooler selectively depending upon which pressure is highest.

5. A compressor unit for supplying and maintaining a compressed working fluid under predetermined superatmospheric pressure and comprising a compressor, a working fiuid intake conduit in flow communication with said compressor, a throttle valve in said intake conduit movable from a first throttle position to a second fully open position and vice versa, a compressed working uid receiver, a compressed working fiuid delivery conduit leading from the compressor to said receiver, a check valve in said delivery conduit, a vent passage communicating with the delivery conduit between the compressor and said check valve, a vent valve in said vent passage movable from a first open position to a second closed position and vice versa, spring means augmented by vent passage pressure arranged for moving said throttle valve and said vent valve from said second positions towards said first positions for unloading the compressor, means responsive to working fluid intake conduit pressure before the throttle valve and vacuum after the throttle valve arranged for moving the throttle valve and vent valve towards said second positions for loading the compressor, and selector valve means arranged to supply compressed working uid to said intake working fluid pressure responsive means upon loading of the compressor for maintaining said pressure responsive means in said second position for maintaining the compressor in loaded condition.

6. A compressor unit (for supplying and maintaining a compressed working fiuid under predetermined superatmospheric pressure and comprising a compressor, a working fluid intake conduit in flow communication with said compressor, a compressor unit) for supplying and maintaining a compressed working fluid under predetermined superatmospheric pressure and comprising a compressor, a workin-g fluid intake conduit in flow communication with said compressor, a throttle valve in said intake conduit movable from a first throttle position to a second fully open position and vice versa, a compressed working fiuid receiver, a compressed working fiuid delivery conduit leading from the compressor to said receiver, a check valve in said delivery conduit, a vent passage communicating with the delivery conduit between the compressor and said check valve, a vent valve in said vent passage movable from a first open position to a second closed position and vice versa, spring means augmented by vent passage pressure arranged for moving said throttle valve and said vent valve from said second positions towards said first positions for unloading the compressor, means responsive to working fiuid delivery pressure and vacuum after the throttle valve arranged for moving the throttle valve and vent valve towards said second positions for loading the compressor, and selector valve means arranged to supply compressed working fiuid to said intake working fluid pressure responsive means upon loading of the compressor for maintaining said pressure responsive means in said second position for maintaining the compressor in loaded condition.

7. A compressor unit for supplying and maintaining a compressed fluid under predetermined superatmosplicric pressure and comprising a compressor having at least two compression stages, an inter cooler between said compression stages, a working fluid intake conduit in flow communication with said compressor, a throttle valve in said intake conduit movable from a first throttle position to a second fully open position and vice versa, a compressed fiuid receiver, a compressed working fluid delivery conduit leading from the compressor to said receiver, a check valve in said delivery conduit, a vent passage communicating with the delivery conduit between the compressor and said check valve, a vent valve in said vent passage movable from a first open position to a second closed position and vice versa, spring means operable to actuate said throttle valve and said vent valve into said first positions, piston means operable to move the throtte valve and the vent into said second positions, a cylinder in which said piston means is disposed, first and second chambers in said cylinder separated by the piston, an auxiliary valve, first and second and intermediate spaces in said auxiliary valve, a double headed auxiliary valve member movable from a position in which said intermediate space communicates with said first space to a position in which the intermediate space communicates with said second space and vice versa, a rst communication from said working fluid intake conduit between the throttle valve and the compressor to said first chamber, a second communication between the first chamber and the first space, a third communication between said intermediate space and said second chamber, a pressure control valve in communication with said receiver, a conduit from said pressure control valve to said auxiliary valve for working pressure fiuid biasing the auxiliary valve member to a position interconnecting the first and intermediate spaces upon attainment of a certain high working fiuid pressure in the pressure control valve to unload the compressor, and a pressure fluid operable means for pressure iiuid biasing the auxiliary valve member to a position interconnecting the second and intermediate spaces upon attainment of a certain low working fiuid pressure in the pressure control valve to load the compressor.

8. A compressor unit according to claim 7, in which the pressure fluid operable means includes a manually operable piston valve device having a valve cylinder, a piston valve movable in said cylinder, a first drain pipe connection, a second pressure fiuid pipe connection, a third operating fluid pipe connection leading to the auxiliary valve, a fourth valve holding pipe connection branched from said third pipe connection for maintaining said piston valve in a position communicating said second and third pipe connections.

9. A compressor unit for supplying and maintaining a compressed fluid under predetermined superatmospheric pressure and comprising a compressor having at least two compression stages, an intercooler lbetween said compression stages, a working fluid intake conduit in fiow communication with said compressor, a throttle valve in said intake conduit movable from a first throttle position to a second fully open position and vice versa, a compressed uid receiver, a compressed working fluid delivery conduit leading from the compressor to said receiver, a check valve in said delivery conduit, a vent passage communicating with the delivery conduit between the compressor and said check valve, a vent valve in said vent passage movable from a first open position to a second closed position and vice versa, spring means operable to actuate said throttle valve and said vent valve into said first positions, piston means operable to move the throttle valve and the vent valve into said second positions, a cylinder in which said piston means is disposed, first and second chambers in said cylinder separated by the piston, an auxiliary valve, a first communication from said working fiuid intake conduit between the throttle valve and the compressor to said first chamber, a second comunication between the first chamber and said auxiliary valve, a third communication between said second chamber and said auxiliary valve, a selector valve dcvice, a selector conduit for connecting said auxiliary valve with said selector valve devi-ce and selectively with the atmosphere or the intercooler depending on which has the highest pressure, a Working fluid pressure actuated switch operably connected to said compressed iluid receiver, a solenoid operated device for selectively connecting the third communication through said auxiliary valve with the second communication when said switch is closed and the solenoid energized for unloading or with said selector conduit when said switch is open and the solenoid consequently deenergized for loading the compressor.

10. A compressor unit according to claim 9, in which said auxiliary valve has rst and second and intermediate spaces, a double headed auxiliary valve member movable from a position in which said intermediate space cornmunicates with said rst space to a position in which the intermediate space communicates with said second space and vice versa, said selector conduit communicating with said second space, a pressure fluid operable means for pressure Huid biasing the auxiliary valve member to a position interconnecting the second space and the intermediate space upon attainment of a certain low working iluid pressure in the receiver causing the pressure switch to close the current through the solenoid and cause the pressure fluid bias of the auxiliary valve member to move said member to compressor loading position.

11. A compressor unit according to claim 9, in which said auxiliary valve is a solenoid operated valve capable of taking a first position in which the solenoid is energized and the valve connects said second and third communications for unloading the compressor and a second position When the pressure swit-ch is opened by maximum pressure in the receiver and the solenoid is deenergized and the valve connects the third communication to the selector conduit for loading the compressor.

12. A compressor unit according to claim 1, in which a cooler is provided in said vent passage, and a cornmunication is arranged from said cooler to the intake conduit.

References Cited UNITED STATES PATENTS 1,968,985 8/1934 Black 230-30 X 2,044,867 6/1936 Woodard 230-24 X 2,213,743 9/ 1940 Miner 230-24 X 2,613,026 10/1952 Banks 230`31 X 2,637,485 5/1953 Yoemans 230-31 X 2,661,145 12/1953 Heineman 230-31 X 3,191,854 6/1965 4I owler et al. 230-24 X 3,255,954 6/ 1966 Norlin et al. 230-31 FOREIGN PATENTS 76,256 4/ 1919 Germany.

DONLEY I. STOCKING, Primary Examiner.

WARREN J. KRAUSS, Assistant Examiner.

Patent Citations
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Referenced by
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US3448916 *Jun 16, 1967Jun 10, 1969Ingersoll Rand CoUnloading system for compressors
US3860363 *May 10, 1973Jan 14, 1975Chicago Pneumatic Tool CoRotary compressor having improved control system
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US4219312 *Oct 20, 1978Aug 26, 1980Hitachi, Ltd.Volume control system for compressor unit
US4227380 *Nov 9, 1979Oct 14, 1980Frick CompanySingle casing, multiple duty valve
US4566863 *Sep 17, 1984Jan 28, 1986Kabushiki Kaisha Toyoda Jidoshokki SeisakushoRotary compressor operable under a partial delivery capacity
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US5358387 *Feb 16, 1994Oct 25, 1994Hitachi Ltd.Oil-free scroll compressor
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US6561766 *Mar 29, 2001May 13, 2003Hitachi, Ltd.Oil free screw compressor operating at variable speeds and control method therefor
US6739841Mar 18, 2003May 25, 2004Hitachi, Ltd.Oil free screw compressor operating at variable speeds and control method therefor
US7607899 *Jul 24, 2003Oct 27, 2009Atlas Copco Airpower, Naamloze VennootschapCompressor with capacity control
US8002527 *Aug 30, 2006Aug 23, 2011Dienes Werke Fur Maschinenteile Gmbh & Co.Dry operating screw-type compressor with pneumatically controlled air relief valve
DE102005040921B4 *Aug 30, 2005Oct 23, 2008Dienes Werke für Maschinenteile GmbH & Co KGTrockenlaufender Schraubenverdichter mit pneumatisch gesteuertem Entlüftungsventil
Classifications
U.S. Classification417/295, 417/290
International ClassificationF04C28/24, F04B49/02, F04C28/02, F04C28/00, F04B25/00, F04B49/24, F04B49/22, F04B49/00
Cooperative ClassificationF04B49/022, F04B49/24, F04C28/02, F04C28/00, F04B49/00, F04B49/225, F04C28/24, F04B25/005
European ClassificationF04B49/00, F04B49/02C, F04B49/24, F04C28/00, F04C28/02, F04C28/24, F04B49/22A, F04B25/00P