CA1140836A - Pneumohydraulic pumping station - Google Patents
Pneumohydraulic pumping stationInfo
- Publication number
- CA1140836A CA1140836A CA000357822A CA357822A CA1140836A CA 1140836 A CA1140836 A CA 1140836A CA 000357822 A CA000357822 A CA 000357822A CA 357822 A CA357822 A CA 357822A CA 1140836 A CA1140836 A CA 1140836A
- Authority
- CA
- Canada
- Prior art keywords
- valves
- control
- air
- directional valves
- pneumohydraulic
- 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.)
- Expired
Links
- 238000005086 pumping Methods 0.000 title claims abstract description 35
- 239000003638 chemical reducing agent Substances 0.000 claims description 7
- 238000010276 construction Methods 0.000 description 8
- 239000012530 fluid Substances 0.000 description 6
- 208000036366 Sensation of pressure Diseases 0.000 description 2
- 150000002500 ions Chemical class 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 241001481828 Glyptocephalus cynoglossus Species 0.000 description 1
- 101100536883 Legionella pneumophila subsp. pneumophila (strain Philadelphia 1 / ATCC 33152 / DSM 7513) thi5 gene Proteins 0.000 description 1
- 101100400378 Mus musculus Marveld2 gene Proteins 0.000 description 1
- 101100240664 Schizosaccharomyces pombe (strain 972 / ATCC 24843) nmt1 gene Proteins 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 229910052729 chemical element Inorganic materials 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000011089 mechanical engineering Methods 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
- F04B9/129—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers
- F04B9/137—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers the pumping members not being mechanically connected to each other
- F04B9/1372—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each pump piston in the two directions is obtained by a double-acting piston fluid motor
- F04B9/1374—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each pump piston in the two directions is obtained by a double-acting piston fluid motor with fluid-actuated inlet or outlet valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/006—Hydraulic "Wheatstone bridge" circuits, i.e. with four nodes, P-A-T-B, and on-off or proportional valves in each link
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
- F01L25/02—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means
- F01L25/04—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means by working-fluid of machine or engine, e.g. free-piston machine
- F01L25/06—Arrangements with main and auxiliary valves, at least one of them being fluid-driven
- F01L25/066—Arrangements with main and auxiliary valves, at least one of them being fluid-driven piston or piston-rod being used as auxiliary valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
- F04B9/129—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers
- F04B9/131—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers with two mechanically connected pumping members
- F04B9/135—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by two single-acting elastic-fluid motors, each acting in one direction
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Pressure Circuits (AREA)
- Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
- Crystals, And After-Treatments Of Crystals (AREA)
Abstract
PNEUMOHYDRAULIC PUMPING STATION
Abstract of the Disclosure The herein-proposed pneumohydraulic pumping station comprises two-position three-way control directional valves featuring two-end differential air piloting and adapted to shfit two-position power directional valves which are intended to control the travel of the sliding member of one of the intensifiers in accordance with the travel of the sliding member of the other intensifier 1. One control chamber of each of the control directional valves is periodically communicated with the source (B) of compressed gas or with the atmosphere through the air chamber of the respective pneumohydraulic inten-sifier . The inlet of each of the control directional valves is communicated with the source (B) of compressed gas, whereas the outlet of one of the control directional valves adapted to shift the power directional valve of one of the intensifiers is so connected to the control chamber of the power directional valve of the other intensifier as to al-ternately communicate the control chamber of the power directional valve of the other intensifier with the source (B) of compressed gas and with the atmosphere.
The pumping station incorporates also air-flow dividing valves one for each of the control directional valves , The outlet of each of the air-flow dividing valves is connected to the other control chamber of the control directional valve so as to switch over the inlet and the outlet thereof depending upon whether a pressure is effective in the air chambers of the respective intensifier .
Fig. 1.
Abstract of the Disclosure The herein-proposed pneumohydraulic pumping station comprises two-position three-way control directional valves featuring two-end differential air piloting and adapted to shfit two-position power directional valves which are intended to control the travel of the sliding member of one of the intensifiers in accordance with the travel of the sliding member of the other intensifier 1. One control chamber of each of the control directional valves is periodically communicated with the source (B) of compressed gas or with the atmosphere through the air chamber of the respective pneumohydraulic inten-sifier . The inlet of each of the control directional valves is communicated with the source (B) of compressed gas, whereas the outlet of one of the control directional valves adapted to shift the power directional valve of one of the intensifiers is so connected to the control chamber of the power directional valve of the other intensifier as to al-ternately communicate the control chamber of the power directional valve of the other intensifier with the source (B) of compressed gas and with the atmosphere.
The pumping station incorporates also air-flow dividing valves one for each of the control directional valves , The outlet of each of the air-flow dividing valves is connected to the other control chamber of the control directional valve so as to switch over the inlet and the outlet thereof depending upon whether a pressure is effective in the air chambers of the respective intensifier .
Fig. 1.
Description
114~836 P~EU~OHYDRAULIC P~MPING S~ATIO~
~ he present in~e~tion rsaltes generally to mechanical engineering and more ~pecifically, to a pneumohydraulic pumping station.
~ he pumping station oi the pre~ent invention i~ mo~t efficiently applicable as variable-displacement pneumo~draul-ic pumping ~tations that have ~ound exten~ive application in a variet~ of industrial branche~ in the capacity of pressure ~ources in hydraulically-operated power actuator~ oi diverse production equipment and machinery, wherein the working speed and force applied to actua ting mechanism~ must be variable in an adequately broad range which is the case in, ~ay, welding and metal-cutting machinery, as well as in rolling mills.
Thi~ i~vention i~ like~ise applicable in industrial equipment and machinery which have to operate under radiation, explosion-hazardous~ hot or chemicals-producing conditions~
~here ele¢tric control circuits cannot be used, as well a~
in the ca~e of ~orking cycles involving prolonged dwelling periods oi the actuating ~ydraulic motors under load, inasmuch as while operatine in such a mode the pneumahydraulic pumping sta~ions ¢onsume no ene-rgy~ and the impelling eleme-nts of the pumping set are ~tationary, i.e., no idle run of the pumping ~tation occurs i~ this case.
ll~V836 One prior-art pneumohydraulic pumping station is hereto-fore known (cf., US Patent No.4,004,420 IPC2 c-lass F15B 15/18, is~ued January 25, 1977) to comprise two pneumo~draulic double-action inten-~ifier~ ha~ing 4ydraulic chambers and variable-volume air chamber3. ~he station also comprises two two-position power-type air directional control valves whose inlets are connected to a compres~_ed ga~ ~ource, while the outlet of each of said valves is connected to the res-pective air chamber of the pneumohydraulic inten~ifier.
~he hydraulic chambers of each intensiiier are communicated, via the 4ydraulic directional control ele_~ents, with the pressure and exhau~t hydraulic lines, to which operating members are also connected. ~he pumping station under dis-cu~sion also comprises two two-position directional pilot valves, each being adapted to change over a respective two-position actua~ing directional control valve which in turn is intended for controlling the traversing of the ~liding member..of one of the intensifier~ in accordance with the tra-versing o~ the sliding member of the other inten~iiier.
~ he afore-discussed known pneumoh~draulic pumping sta-tion, however, fails to a~oid the appearance of spurious signals in the pneumatic control circuit of the pneumobydra-ulic intensifiers, comprising two-position power and control 1~4U836 directional valve~ and eleme~ts gover~ng the compressed-gas pressure in ~he compre~sed-ga~ lines.
Spuriou~ signals that are liable to appear i n the pump-ing station in ques~ion are in iact compressed-gas pressure signals (pulses) th~t arrive at the control chambers of the two-position power directional ~alves due to mistimed ~w~tching over of the two-po~ition oontrol directional valves, which in cur~ may occur owing to the fact that pressure in the control chambers of said directional valves i~ reli~ved through the two-position power directional valve communicated in this ca~e wlth the intensifler air chamber being exhausted.
It is due to a po~sibile appearance o~ such spuriou~
sign~ls in the cour~e oi the pumping ~tation operation that substantial hydraulic fluid pressure fluctuations may occur in the h~draulic pressure line thereof and that full delivery strokes oi the intensiiier sliding members are not alwa~s attained.
As a re~ult, rather irequent switching over oi all the devices oi the control system are liable to occur, which aifects adversely the eificiency and service lii oi the pump~ng station.
It is a primary and essential object of the present invention to provide a pneumo4ydraulic pumping station, where-~, .. .
l~V836 in the air-operated control system thereo~ would be so arra-nged aæ to preclude the arrival of spurious signals at the control chamber~ o~ two-position power directional valves.
It i8 another as much essential object of the present invention to provide a pneumohydraulic pumping station that wou~ be instrumental in obtaining more stable peroformance characteristics as to the hydraulic fluid pressure effective at the inlet of the hydraulic actuator.
Said objects are accomplished in a pneumohydraulic pumping station, compxising at least two double-action pneumohy-draulic intensi~ier, the variable-volume air chambers o~ each o~ said inten~i~iers being connected to the outlets of two-position power directional valves while the inlet of each of said valves is ¢onnected to a compreæsed-ga~ source, where-a~ the hydraulic chambers of said double-action pneumohydra-ulic intensifier~ are communicated, via hydraulic directional control element9, with bhe preæsure and e~haust lines to which the actuatoræ are co~nected~ and two two-position control directional valves, each of them being adapted to switch over a respective two-position power directional valve inten-ded, in turn, to control the travel o~ the sliding member o~
one of the inten~ifiers in a preset concordance with the tra-vel of the sliding member o~ the other intensifier,.said pumping station having, according to the invention, ~ome other two-position control directional valve~ adapted to switch two-po~ition power directional valve~ at a preset moment of the working cycle, said other directional valve~ being provi-ded with one for each of the pneumoh~draulic intensifier~, use being therein madel as said two-position control valves and other such valves, o~ two-po~ition three-way control di-rectional valves featuring two-end compressed-air piloting, each o~ ~aid valves having two control chambers for switch-ing over its inlet and outlet, one of said control chamber~ of each of the two-position three-wny control directional valves being adapted to periodically communicate, through the air chamber of a respective pneumohydraulic intensifier~ with the source o~ compressed gas or the atmosphere, the inlet thereof is communicated with the source of compressed gas, and the outlet of said two-position three-way control directi-onal valve3 adapted to switch over the two-position power di-rectional valve of one of the pneumohydraulic intensifier~
is ~o connected to the control chamber o~ the two-po~ition power directional valve of the other pneumohydraulic intensi-fier as to alternatively communicate the control chamber of the two-position power directional valve of the other pneumohyd-raulic intensifier with the source of compressed gas and the atmosphere; in addition, said p~mping ~tation incorporates a 11~()836 number of air-flow dividing, valves, one for each of the two-position three-way control directional valve~, the outlet of each of said air-flow dividing valves being connected to the other control chamber of each of the two-po~ition three-way control directional valve so as to switch over its inlet and outlet depending upon whether a pressure is effective in the air chambers of a respective pneumohydraulic intensi~ier; one of the inlets of one of said air-~low dividing valves of one of the two-position three-way control directional valve~ of each pneumohydraulic inten~ifier is connected, via a direc-tional element, to the air chamber of the same pneumohydraulic intensifier, and to the outlet of the two-po~ition power di-rectional valve thereo~, whereas the other inlet is connected to the source of compressed gas through a pressure reducer valve, while the other control chamber of one of the two-position three-way control directional valves is communicated, through one of the ;nlets of one of the flow dividing valves, with the outlet o~ the two-position power directional valve and with the source of compressed gas, and one of the inlets of the other air-flow dividing valve of the other two-position three-way control directional valve o~ the same pneumohydrau-lic intensifier is connected to the source of compressed gas through a directional element and a pressure reducer valve, while the other inlet thereof is connected to the air chamber of the same intensifier and to the outlet of it~ two-position power directional valve; the other control chamber o~ the other two-position three-way control directional valve of the same pneumohydraulic intensi~ier i~ communicated, via the other inlet of other air-operated splitter valve, with the outlet o~ its two-position power directional valve and with the source of compre~sed gas or the atmosphere.
It i~ due to the afore-discussed circuitry of the pneu-matic control system of the proposed pumping station that spurious pressure signals (pulses) are pre¢luded, said signals being shaped by the two-po~ition directional valves and arriving in the control chambers of the air-operated power directional valves.
It is thanks to the a~ore-disclosed embodiment of the two-position control directional valves and their being connected to the air-operated control s~stem o~ the hydro-pneumatic intensifiers that said two-position directional valves operate in due time and alternatively. This in turn provides ~or timely alternate operatio~ of the two-position power directional valves, whereby no spurious signals occur i~ the air-operated control ~ystem, delivered ~rom the two-po~ition control air-operated directio~al valves to the con-trol chambers of the two-po~ition power directional valves.
On the other hand freedom from spuriou3 signals is attained also on account of the Pact that, when a required sig-nal is delivered, an adequately accurate and timely switching over the two-position air-operated control directional val-ves occurs even iP a residual.preqsure is effective in the intensifier air chambers.
~ he herein-proposed pneumohydraubic pumping station provide~ for more stable pre~sure applied by ~aid ~tation to the hydraulic actuator, and feature~ higher efPiciency~ since it i~q due to the absence of spurious signals i~ the circuit that full strokes of the intensifier sliding member~ are effected to deliver the hydraulic fluid.
Said embodiment of the proposed pneumohydraulic pumping station aPPords more reliable operation thereof as compared to the known pumping station, thiR being due to the fact that the numbor of switch-over cycles of the devices incor-porated into the air-operated control sy~qtem as well as the number of reversals of the intensifier i~ much reduced, Thi~
in turn contributes to ex*ended service life of the p~eumo-hydraulic pumping station.
It ensueR from the hereinabove diqcussed that the pneu-mohydraulic pumping station provided according to the present invention features rather high technical and economical characteri~tic as compared to the prior-art one and assures reliable operation of the actuators of production equipment ~ ;. , "' ~
" , ~
:;
~l~V836 items connected to said pumping ~tation.
Given below i~ a detailed de~cription o~ a ~pecific exemplary embodiment of the pre3ent invention to be read in conjunction with the attached drawing, wherein a schematic diagram of the proposed pneumohydraulic pumping statian is represented.
The pneumohydraulic pumping station, according to the pre~ent invention, comprises two double-action pneumoh~-draulic intensifiers 1 of any construction suitable for the purpose.
Each o~ the intensifiers 1 has variable-volume air cham-bers 2 with control ports 2a and 2b, hydraulic chambers 3 and a sliding member 4 made essentially as a piston 4 mounted in the housing of the intensifier 1 ~or reciprocation.
~ he hydraulic chambers 3 of the intensifiers 1 are com-municated with a pressure line 5 and a~ exhaust line 6 via hydraulic directional elements which are in ef~ect bridge~ 7 of hydraulic check valves 8a9 8b, 8c and 8d of the an~ known construction.
Connected to the lines 5 and 6 is an actuator A which may be made as a hydraulic motor.
~ he hydraulic chambers 3 o~ the intensifier~ 1 are also 1~4~)~336 communicated with pilot-operated hydraulic check valves 9, 10, 11, 12 which are adapted to communicate the hydraulic chambers 3 with the exhaust line 6 and with a pneumohydraul~c flow equalizer 13 ha~ing any construction suitable ~or the purpose.
~ he pilot-operated hydraulic check valve3 9, 10, 11, 12 and the flow equalizer 13 are adapted to balance a dif-~erence between the amount of ~luid delivexed to the pressu-re line 5 and that retur~ed aloDg the e~haust line 6.
Re~pective inlet~ 9a, lOa, lla, 12a of the h~draulic check valves 9, 10~ 11, 12 are connected to the outlet of the flow equalizer 13 whoQe inlet 13a i9 con~ected to an air pressure reducing valve 14 o~ a known construction, which i~ communicated, through its inlet~ with a compressed ga~
source B.
Outlets 9b, lOb, llb, 12b of the respective valves 9, 10,11, 12 are communicated with the respective hydraulic chambers 3 o~ the intensifiers 1.
The valve~ 9, 10, 11, 12 have also co~trol chambers 9c~
lOc, llc, 12c each of which i~ communicated with the one o~
the h~draulic chamber~ 3, whereto the inlet of said valve 9, or 10, or 11, or 12 is not con~ected.
The pneumohydraulic pumping unit comprise9 also two .~ ' .
)836 two-position power directional valves 15 having two-end compressed-air piloting and featuring any construction sui-table ior the purpose.
The directional valves 15 s~rve to ~eed compressed gaS
~rom the sourco B to the air chambers 2 of the intensifiers 1, i.e., they are adapted to control the travel of the sliding member 4 of one of the in~en~ifiers 1 in a preset concordance with the travel of the sliding member 4 of the other intenL~-si~ier 1.
Each of tho power directional valves 15 has two control chambers 15a and 15b, an inlet 15c and outlets 15 d and 15e.
~ he chambers 15a and 15b are for switching over the ports of the directional valves 15 and ~or alternatively ~eed-ing compressed gas to the air chambers 2 of the intensifiers 1.
~ he pneumohydraulic pumping station has also main two-position control directibnal valves 16 and additional two-position control directional valves 17, one of each type per intensi~ier 1, said directional valves 16 and 17 being intended for ~witching over the power directional valves 15.
~ore exactly, the control directional valves 16 and 17 are adapted to send a pressure pulse to the control chambers 15a, 15b of the power ~rectional valves so as to swltch-over the outlets 15d and 15e thereo~.
According to the present invention, the control direc-114~)836 -- 12 .
tional valves 16 and 17 are e~sentially two-position three-way control directional valves ~eaturing two-end differenti-al compres9ed-air piloting a~d having a known con~truction.
Con~oint u~e o~ the control directional valve~ 16 and 17 provides ~or ~witching orer of the power directional val-ves 15 at a preset moment of the cycle.
~ ach o~ the directional valves 16 and 17 has two con-trol chambers 16a~-16b, and 17a, 17b, repsectivel~, a res-pective inlet 16c, 17c, and a respective outlet 16d, 17d.
~he chambers 16a~ 16b, 17a,17b are adapted ~or switching over said lnlets 16c, 17c and said outlets 16d, 17d.
~ he chamber 16a, 17a of the respective directional val-ves 16 and 17 is adapted to periodically communicate, through the respective air chamber 2 of the intesi~ier 1, with the source B of compressed gas~ or with the atmosphere.
~ he inlets 16c, 17c of each of the two-position control air directional valves 16 and 17 are connected to the compre-ssed gas source B, whereas the outlets 16d, 17d of the two-position co~trol air directional valves 16, 17 of one of the intensi~iers 1 are communicated with the control chambers 15a~
15b of the two-position air dlrectional valve 15 of the other intenslfier 1 QO that the outlet~ 16d, 17d alternatel~
communicate the control chamber 15a or 15 b of the po~er di-. - .
-V~336 -- 13 _ rectional valve 15 of the other inten~ifier 1 with the compre~sed gas source B and with the atmoqphere.
~ he pumping station, according to the i~vention also ha8 airflow dividing valves l8, 19, 20, 21, one for each of the control directional valveq 16, 17 adapted to switch over the inlets 16c, 17c ~nd the outlets 16 d, 17d of said valves depending upon whether a pressure i~ effective in air cham_ bers 2 of the re~pective intensifier lo Each of the air-flow dividing avalves 18, 19, 20, 21 is of the heretofore-known construction and incorporates one inlet 18a, l~a, and 20a, 21a, and the other inlet 18b, l9b, and 20b, 21b, as well as an outlet 18c, l9c, 20c, 21c~ res-pectively.
A directional element 22 is provided at the former inlets 18a, 20a o~ the air-~low dividing valves 18, 20, res-pectively, said element being in fact an air-operated check valve indicated at the same Ref.No.22 and having an known construction suitable for the purpose.
On inlets 18a, 20 of the air-operated i~olating valves 18, 20 of the two-position three-way co~trol diredtional valve 16 o~ each intensifier 1 are connected, via the air-operated check valves 22, to the air chamber 2 of the inten~lfier 1 and to the outlets 15d of the power directional valve 15 thereof.
~ he other inlets 18b~ 20b of the air-flow dividing valves ll9~V836 18 and 20 are connected to the compre~sed gas source B
through a pressure regulator 23.
~ he pressure regulator 23 is in ~act an air reducing valve andicated at the same Ref.No.23 having a~y of the known constructions suitable for the purpose.
~ he other control chamber 16b of one of the two-position three-way control directional valves 16 i~ communicated9 thro-ugh one inlet 18a, 20a o~ one air-operated isolating valve 18, 20, with the outlet 15d of the two-position power di-rectional valve 15.-~ ne inlet~ l9a, 21a of the other air-operated isolating valves 19, 21 of the other two-position control directional valve 17 of each intensifier 1 are connected, via the direc-tional element 22 and the pressure reducer 23, to the com-pressed gas ~o~rce B.
~ he other inlets l9b, 21b thereof are connected to the air chamber 2 of the same inten~ifier 1 and to the outlets 15e of the power directional valves 15.
` ~-he other control chamber 17b of tho other three-~ay control directional valve 17 i3 communicated, through the other inlet~ 19b, 21b of the air-operated isolating valves 19, 21, through the outlet 15O of the power directional valve~ 15 thereof, with the compressed gas source B, or with the atmosphere.
~40836 ~ he outlet~ 18c, 19c, 20c, 21c of each o~ the air-operated valves 18, 19, 20, 21 are connected to the other control chamber ~6b, 17b o~ the control directional valves 16, 17 so as to ~witch over their inlets 16c, 17c and outlets 16d, 17d depending upon ~hether a pres~ure i5 present in ~he air chamber~ 2 o~ the intensifier 1.
~ he pneumohydraulic pumping tabion di~closed in the present invention operates as follow~
Upon putting the pumping ~tat1on in operation com-pressed gas is force-fed ~rom the source B to the inlets 15c o~ the two-position air-operated power directional valve~ 15, and further on through the ports thereof to the right-hand (as viewed in the drawing~ air chambers 2 of the intensifiers 1.
As it can be see~ ~rom the drawing the piston 4 of the left-hand intensifier 1 a~sume~ it~ rightmost po~ition, while the p~ston 4 of the right-hand intensifier 1 is in the leftmost position. The air pressure pulse (signal). i~
delivered ~rom the outlet 15e of the left-hand (as seen in the drawing~ two-position power directional valve 15 .
through the air-flow dividing valve 19 to the control chamber 17b of the other control air directional valve 17, thus switching it over to the position, wherein the control cha~ber 15b of the two-position power directional valve 15 (the right-hand one as seen .
., in the drawing) is communicated with the atmosphere.
As a re~ult, the air pressure pulse is delivered ~rom the outlet of the air pressure reducer valve 23 through the inlet 18b of the air-flow dividing valve 18 to the control chamber 16b o~ the two-position control air directional valve 16 to switch it over to the right-hand position, inas-much as its le~-hand control chamber 16a is communicated with the atmo~phere through the le~t-hand air chamber o~ the intensifier 1 and via the two-position power directional valve 15.
In this case the right-hand (as seen in the drawing) control chamber 15b of the two-position power dlrectional valve 15 (the right-hand as seen in the drawing) i9 commu-nicated with the atmosphere. Then the air pressure pulse is delivered ~rom the outlet 15e of the right-hand (as in the drawing) two-position power directional valve 15 through the inlet 21b of the air-flow dividing valve 21 to the chamber 17b of the other control air directional valve 17 to shift it to the rightmost position, inas~uch as the air pressure pulse arriving in the chamber 17a of the control air di-rectional valve 17 from the air chamber 2 of the right-hand (as in the drawing) intensifier 1 is applied to a ~maller effective area of the directional element (not shown) of the control chamber 17a. As a result the control chamber 15c ~ .
-1~4C~836 of the left-hand (as seen in the drawing) two-position power directional valve 15 is communicated with the atmosphere.
~hen the air pressure pulse is delivered from the outlet of the air pressure reducer valve 23 through the air-~low dividing valve 20 and the inlet 20b to the control chamber 16b of the right-hand (as in the drawing) control directional valve 16.
At the same time compressed gas is ~orce-fed from the air chamber 2 of the right-hand (as seen in the drawing) în-tensifier 1 to ths control chamber 16a o~ the samo directional valve, with the result that the right-ha~d (as seen in the drawing) control air directional valve 16 i3 shi~ted to the position, wherein an air pressure pulse appears at the out-let 16d thereof and i9 then delivered to the control chamber 15b of the left-hand (as seen in the drawing) two-position power directional valve 15, whereas its directional element remains in tho same position.
Thu~, the piston 4 of the right-~and (as seen in the drawing) intensifier 1 is kept in the leftmost position, whereas the piston 4 of the left-hand (as see~ in the drawing~
intensifier 1 starts travelling to the left, thereby dis-placing the hydraulic fluid from the left-hand hydraulic chamber 3 of the left-hand (as seen in the drawingj inten-si~ier 1 through the hydraulic check valve 8a of the left-hand , (as seen in the drawing) hydraulic bridge 7 to the pressure hydraulic line 5 and further on to the hydraulic actuator A.
The outflow of the hydraulic ~luid ~rom the hydraulic actuator A i8 effected through the hydraulic exhaust line 6 and Yurther on through the hydraulic check valve 8c of the left-hand (as seen in the drawing) hydraulic bride 7 to the right-hand hydraulic chamber 3 of the left-hand (as seen in the drawing) intensifier 1. As the piston 4 of the intensi-fier 1 passes on the right-hand control port 2b an air pres-sure pulse appears in the latter, which is then delivered to the control chamber 17a of the other control directional valve 17 (the left-hand one as seen in the drawing)~ which in this case remains in the right-hand position since an air pres~ure pulse appears in it3 control chamber 17b having a larger-area directional element (not shown), said air pres-sure pulse being sent from the outlet 15e of the left-hand (as seen in the drawing) two-position power directional valve 15.
As the pi~ton 4 of the intensifier 1 passes on the left-hand control port 2a of the intensifier 1, an air pressure pulse appears in the latter, which arrives then in the con-trol chamber }6a of the main control directional valve 16 (the left-hand one a~ seen in the drawing) and overcomes the force of pressure of compressed gas effective in the ~ .
: ; ' ~ ` , 114V83~
control chamber 16b, said gas being delivered from the air pres~ure reducing valve 23 through the port 18b of the air-flow dividing valve 18.
Thus, the control directional valve 16 i8 shifted to the left-hand (as seen in the drawing) position, and an air pressure pulse appears at the outlet 16d thereof, said pulse then arriving in the control chamber 15a of the right-hand (as seen in the drawing) two-position power directional valve 15 to shift the latter to the left-hand position.
Next, the piston 4 of the right-hand (as seen in the dra-wing) intensifier 1 starts travelling to the right, whereas the piston 4 of the left-hand (as seen in the drawing) intensifier 1 keeps travelling to the left.
As soon as the right-hand (as seen in the drawing) two-position power directional ~alve 15 is shifted to the left an air pressure pulse is delivered from its outlet 15d through the air-flow dividing valve 20 to the control chamber 16b of the main control air directional valve 16 to shift the latter to the position, wherein the control chamber 15b of the left-hand (as seen in the drawing) two-position power directional valve 15 is communicated with the atmosphere, whereby said directional valve is prepared for reversal.
In the course of joint tra~elling the piston 4 of the left-hand (as seen in the drawing) intensifier 1 come~ to ".
~.
114~836 the left-hand ~top ~not shown), whereas the pi8ton 4 of the other intensifier 1 passes on the left-hand control port 2a of the intensifier 1, In thi3 case the main control air directional valve 16 (the right-hand one as seen in the drawing) remain~ in the right-hand position, Next, the piston 4 of the right-hand (as seen in the drawing) intensifier 1 passes on the right-hand control port 2b, ~ he air pressure pulse appearing at the outlet of said port shïft~ the right-hand (as seen in the drawing) control air directional valve 17 to the position, wherein an air pres~ure pulse is delivered from its outlet 17d to the control chamber 15a of the left-hand (as seen in the drawing) two-position power directional valve, and compressed ~as fed from the source B is delivered from its outlet 15d to the air cham-ber 2 of the left-hand (as seen in the drawing) intensifier 1.
As a result the piston 4 of said inten~ifier 1 begins travelling to the right concurrently with the right-hand travel of the piston 4 of the other intensifier 1.
The balancing of the difference between the amount of the hydraulic fluid discharged into the pressure line 5 and that of said fluid returned to the exhaust line 6 is e~fected by the system, incorporating the bridges 7 of the hydraulic check valves 8, 9 and the flow equalizer 13 with the air pre~sure reducing valve 14.
.
' .
-. . .
.
~ ora~much a~ residual pre~ure in the air chambers 2 i~
blocked during each reversal of the inten~i~iers 1 by the pressure permanently admitted through the air pressure reducing valve 23 to the control chambers 16b, 17b of the control air directional valves 16, 17, no spurious air pressure signals and hence no false switching-over of the two-positional valves 15 occur.
The pilot mo~el of the proposed pneumodydraulic station has passed comprehensive tests that confirm high efficiency and reliability of the propo~ed pumping station.
~ he present in~e~tion rsaltes generally to mechanical engineering and more ~pecifically, to a pneumohydraulic pumping station.
~ he pumping station oi the pre~ent invention i~ mo~t efficiently applicable as variable-displacement pneumo~draul-ic pumping ~tations that have ~ound exten~ive application in a variet~ of industrial branche~ in the capacity of pressure ~ources in hydraulically-operated power actuator~ oi diverse production equipment and machinery, wherein the working speed and force applied to actua ting mechanism~ must be variable in an adequately broad range which is the case in, ~ay, welding and metal-cutting machinery, as well as in rolling mills.
Thi~ i~vention i~ like~ise applicable in industrial equipment and machinery which have to operate under radiation, explosion-hazardous~ hot or chemicals-producing conditions~
~here ele¢tric control circuits cannot be used, as well a~
in the ca~e of ~orking cycles involving prolonged dwelling periods oi the actuating ~ydraulic motors under load, inasmuch as while operatine in such a mode the pneumahydraulic pumping sta~ions ¢onsume no ene-rgy~ and the impelling eleme-nts of the pumping set are ~tationary, i.e., no idle run of the pumping ~tation occurs i~ this case.
ll~V836 One prior-art pneumohydraulic pumping station is hereto-fore known (cf., US Patent No.4,004,420 IPC2 c-lass F15B 15/18, is~ued January 25, 1977) to comprise two pneumo~draulic double-action inten-~ifier~ ha~ing 4ydraulic chambers and variable-volume air chamber3. ~he station also comprises two two-position power-type air directional control valves whose inlets are connected to a compres~_ed ga~ ~ource, while the outlet of each of said valves is connected to the res-pective air chamber of the pneumohydraulic inten~ifier.
~he hydraulic chambers of each intensiiier are communicated, via the 4ydraulic directional control ele_~ents, with the pressure and exhau~t hydraulic lines, to which operating members are also connected. ~he pumping station under dis-cu~sion also comprises two two-position directional pilot valves, each being adapted to change over a respective two-position actua~ing directional control valve which in turn is intended for controlling the traversing of the ~liding member..of one of the intensifier~ in accordance with the tra-versing o~ the sliding member of the other inten~iiier.
~ he afore-discussed known pneumoh~draulic pumping sta-tion, however, fails to a~oid the appearance of spurious signals in the pneumatic control circuit of the pneumobydra-ulic intensifiers, comprising two-position power and control 1~4U836 directional valve~ and eleme~ts gover~ng the compressed-gas pressure in ~he compre~sed-ga~ lines.
Spuriou~ signals that are liable to appear i n the pump-ing station in ques~ion are in iact compressed-gas pressure signals (pulses) th~t arrive at the control chambers of the two-position power directional ~alves due to mistimed ~w~tching over of the two-po~ition oontrol directional valves, which in cur~ may occur owing to the fact that pressure in the control chambers of said directional valves i~ reli~ved through the two-position power directional valve communicated in this ca~e wlth the intensifler air chamber being exhausted.
It is due to a po~sibile appearance o~ such spuriou~
sign~ls in the cour~e oi the pumping ~tation operation that substantial hydraulic fluid pressure fluctuations may occur in the h~draulic pressure line thereof and that full delivery strokes oi the intensiiier sliding members are not alwa~s attained.
As a re~ult, rather irequent switching over oi all the devices oi the control system are liable to occur, which aifects adversely the eificiency and service lii oi the pump~ng station.
It is a primary and essential object of the present invention to provide a pneumo4ydraulic pumping station, where-~, .. .
l~V836 in the air-operated control system thereo~ would be so arra-nged aæ to preclude the arrival of spurious signals at the control chamber~ o~ two-position power directional valves.
It i8 another as much essential object of the present invention to provide a pneumohydraulic pumping station that wou~ be instrumental in obtaining more stable peroformance characteristics as to the hydraulic fluid pressure effective at the inlet of the hydraulic actuator.
Said objects are accomplished in a pneumohydraulic pumping station, compxising at least two double-action pneumohy-draulic intensi~ier, the variable-volume air chambers o~ each o~ said inten~i~iers being connected to the outlets of two-position power directional valves while the inlet of each of said valves is ¢onnected to a compreæsed-ga~ source, where-a~ the hydraulic chambers of said double-action pneumohydra-ulic intensifier~ are communicated, via hydraulic directional control element9, with bhe preæsure and e~haust lines to which the actuatoræ are co~nected~ and two two-position control directional valves, each of them being adapted to switch over a respective two-position power directional valve inten-ded, in turn, to control the travel o~ the sliding member o~
one of the inten~ifiers in a preset concordance with the tra-vel of the sliding member o~ the other intensifier,.said pumping station having, according to the invention, ~ome other two-position control directional valve~ adapted to switch two-po~ition power directional valve~ at a preset moment of the working cycle, said other directional valve~ being provi-ded with one for each of the pneumoh~draulic intensifier~, use being therein madel as said two-position control valves and other such valves, o~ two-po~ition three-way control di-rectional valves featuring two-end compressed-air piloting, each o~ ~aid valves having two control chambers for switch-ing over its inlet and outlet, one of said control chamber~ of each of the two-position three-wny control directional valves being adapted to periodically communicate, through the air chamber of a respective pneumohydraulic intensifier~ with the source o~ compressed gas or the atmosphere, the inlet thereof is communicated with the source of compressed gas, and the outlet of said two-position three-way control directi-onal valve3 adapted to switch over the two-position power di-rectional valve of one of the pneumohydraulic intensifier~
is ~o connected to the control chamber o~ the two-po~ition power directional valve of the other pneumohydraulic intensi-fier as to alternatively communicate the control chamber of the two-position power directional valve of the other pneumohyd-raulic intensifier with the source of compressed gas and the atmosphere; in addition, said p~mping ~tation incorporates a 11~()836 number of air-flow dividing, valves, one for each of the two-position three-way control directional valve~, the outlet of each of said air-flow dividing valves being connected to the other control chamber of each of the two-po~ition three-way control directional valve so as to switch over its inlet and outlet depending upon whether a pressure is effective in the air chambers of a respective pneumohydraulic intensi~ier; one of the inlets of one of said air-~low dividing valves of one of the two-position three-way control directional valve~ of each pneumohydraulic inten~ifier is connected, via a direc-tional element, to the air chamber of the same pneumohydraulic intensifier, and to the outlet of the two-po~ition power di-rectional valve thereo~, whereas the other inlet is connected to the source of compressed gas through a pressure reducer valve, while the other control chamber of one of the two-position three-way control directional valves is communicated, through one of the ;nlets of one of the flow dividing valves, with the outlet o~ the two-position power directional valve and with the source of compressed gas, and one of the inlets of the other air-flow dividing valve of the other two-position three-way control directional valve o~ the same pneumohydrau-lic intensifier is connected to the source of compressed gas through a directional element and a pressure reducer valve, while the other inlet thereof is connected to the air chamber of the same intensifier and to the outlet of it~ two-position power directional valve; the other control chamber o~ the other two-position three-way control directional valve of the same pneumohydraulic intensi~ier i~ communicated, via the other inlet of other air-operated splitter valve, with the outlet o~ its two-position power directional valve and with the source of compre~sed gas or the atmosphere.
It i~ due to the afore-discussed circuitry of the pneu-matic control system of the proposed pumping station that spurious pressure signals (pulses) are pre¢luded, said signals being shaped by the two-po~ition directional valves and arriving in the control chambers of the air-operated power directional valves.
It is thanks to the a~ore-disclosed embodiment of the two-position control directional valves and their being connected to the air-operated control s~stem o~ the hydro-pneumatic intensifiers that said two-position directional valves operate in due time and alternatively. This in turn provides ~or timely alternate operatio~ of the two-position power directional valves, whereby no spurious signals occur i~ the air-operated control ~ystem, delivered ~rom the two-po~ition control air-operated directio~al valves to the con-trol chambers of the two-po~ition power directional valves.
On the other hand freedom from spuriou3 signals is attained also on account of the Pact that, when a required sig-nal is delivered, an adequately accurate and timely switching over the two-position air-operated control directional val-ves occurs even iP a residual.preqsure is effective in the intensifier air chambers.
~ he herein-proposed pneumohydraubic pumping station provide~ for more stable pre~sure applied by ~aid ~tation to the hydraulic actuator, and feature~ higher efPiciency~ since it i~q due to the absence of spurious signals i~ the circuit that full strokes of the intensifier sliding member~ are effected to deliver the hydraulic fluid.
Said embodiment of the proposed pneumohydraulic pumping station aPPords more reliable operation thereof as compared to the known pumping station, thiR being due to the fact that the numbor of switch-over cycles of the devices incor-porated into the air-operated control sy~qtem as well as the number of reversals of the intensifier i~ much reduced, Thi~
in turn contributes to ex*ended service life of the p~eumo-hydraulic pumping station.
It ensueR from the hereinabove diqcussed that the pneu-mohydraulic pumping station provided according to the present invention features rather high technical and economical characteri~tic as compared to the prior-art one and assures reliable operation of the actuators of production equipment ~ ;. , "' ~
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:;
~l~V836 items connected to said pumping ~tation.
Given below i~ a detailed de~cription o~ a ~pecific exemplary embodiment of the pre3ent invention to be read in conjunction with the attached drawing, wherein a schematic diagram of the proposed pneumohydraulic pumping statian is represented.
The pneumohydraulic pumping station, according to the pre~ent invention, comprises two double-action pneumoh~-draulic intensifiers 1 of any construction suitable for the purpose.
Each o~ the intensifiers 1 has variable-volume air cham-bers 2 with control ports 2a and 2b, hydraulic chambers 3 and a sliding member 4 made essentially as a piston 4 mounted in the housing of the intensifier 1 ~or reciprocation.
~ he hydraulic chambers 3 of the intensifiers 1 are com-municated with a pressure line 5 and a~ exhaust line 6 via hydraulic directional elements which are in ef~ect bridge~ 7 of hydraulic check valves 8a9 8b, 8c and 8d of the an~ known construction.
Connected to the lines 5 and 6 is an actuator A which may be made as a hydraulic motor.
~ he hydraulic chambers 3 o~ the intensifier~ 1 are also 1~4~)~336 communicated with pilot-operated hydraulic check valves 9, 10, 11, 12 which are adapted to communicate the hydraulic chambers 3 with the exhaust line 6 and with a pneumohydraul~c flow equalizer 13 ha~ing any construction suitable ~or the purpose.
~ he pilot-operated hydraulic check valve3 9, 10, 11, 12 and the flow equalizer 13 are adapted to balance a dif-~erence between the amount of ~luid delivexed to the pressu-re line 5 and that retur~ed aloDg the e~haust line 6.
Re~pective inlet~ 9a, lOa, lla, 12a of the h~draulic check valves 9, 10~ 11, 12 are connected to the outlet of the flow equalizer 13 whoQe inlet 13a i9 con~ected to an air pressure reducing valve 14 o~ a known construction, which i~ communicated, through its inlet~ with a compressed ga~
source B.
Outlets 9b, lOb, llb, 12b of the respective valves 9, 10,11, 12 are communicated with the respective hydraulic chambers 3 o~ the intensifiers 1.
The valve~ 9, 10, 11, 12 have also co~trol chambers 9c~
lOc, llc, 12c each of which i~ communicated with the one o~
the h~draulic chamber~ 3, whereto the inlet of said valve 9, or 10, or 11, or 12 is not con~ected.
The pneumohydraulic pumping unit comprise9 also two .~ ' .
)836 two-position power directional valves 15 having two-end compressed-air piloting and featuring any construction sui-table ior the purpose.
The directional valves 15 s~rve to ~eed compressed gaS
~rom the sourco B to the air chambers 2 of the intensifiers 1, i.e., they are adapted to control the travel of the sliding member 4 of one of the in~en~ifiers 1 in a preset concordance with the travel of the sliding member 4 of the other intenL~-si~ier 1.
Each of tho power directional valves 15 has two control chambers 15a and 15b, an inlet 15c and outlets 15 d and 15e.
~ he chambers 15a and 15b are for switching over the ports of the directional valves 15 and ~or alternatively ~eed-ing compressed gas to the air chambers 2 of the intensifiers 1.
~ he pneumohydraulic pumping station has also main two-position control directibnal valves 16 and additional two-position control directional valves 17, one of each type per intensi~ier 1, said directional valves 16 and 17 being intended for ~witching over the power directional valves 15.
~ore exactly, the control directional valves 16 and 17 are adapted to send a pressure pulse to the control chambers 15a, 15b of the power ~rectional valves so as to swltch-over the outlets 15d and 15e thereo~.
According to the present invention, the control direc-114~)836 -- 12 .
tional valves 16 and 17 are e~sentially two-position three-way control directional valves ~eaturing two-end differenti-al compres9ed-air piloting a~d having a known con~truction.
Con~oint u~e o~ the control directional valve~ 16 and 17 provides ~or ~witching orer of the power directional val-ves 15 at a preset moment of the cycle.
~ ach o~ the directional valves 16 and 17 has two con-trol chambers 16a~-16b, and 17a, 17b, repsectivel~, a res-pective inlet 16c, 17c, and a respective outlet 16d, 17d.
~he chambers 16a~ 16b, 17a,17b are adapted ~or switching over said lnlets 16c, 17c and said outlets 16d, 17d.
~ he chamber 16a, 17a of the respective directional val-ves 16 and 17 is adapted to periodically communicate, through the respective air chamber 2 of the intesi~ier 1, with the source B of compressed gas~ or with the atmosphere.
~ he inlets 16c, 17c of each of the two-position control air directional valves 16 and 17 are connected to the compre-ssed gas source B, whereas the outlets 16d, 17d of the two-position co~trol air directional valves 16, 17 of one of the intensi~iers 1 are communicated with the control chambers 15a~
15b of the two-position air dlrectional valve 15 of the other intenslfier 1 QO that the outlet~ 16d, 17d alternatel~
communicate the control chamber 15a or 15 b of the po~er di-. - .
-V~336 -- 13 _ rectional valve 15 of the other inten~ifier 1 with the compre~sed gas source B and with the atmoqphere.
~ he pumping station, according to the i~vention also ha8 airflow dividing valves l8, 19, 20, 21, one for each of the control directional valveq 16, 17 adapted to switch over the inlets 16c, 17c ~nd the outlets 16 d, 17d of said valves depending upon whether a pressure i~ effective in air cham_ bers 2 of the re~pective intensifier lo Each of the air-flow dividing avalves 18, 19, 20, 21 is of the heretofore-known construction and incorporates one inlet 18a, l~a, and 20a, 21a, and the other inlet 18b, l9b, and 20b, 21b, as well as an outlet 18c, l9c, 20c, 21c~ res-pectively.
A directional element 22 is provided at the former inlets 18a, 20a o~ the air-~low dividing valves 18, 20, res-pectively, said element being in fact an air-operated check valve indicated at the same Ref.No.22 and having an known construction suitable for the purpose.
On inlets 18a, 20 of the air-operated i~olating valves 18, 20 of the two-position three-way co~trol diredtional valve 16 o~ each intensifier 1 are connected, via the air-operated check valves 22, to the air chamber 2 of the inten~lfier 1 and to the outlets 15d of the power directional valve 15 thereof.
~ he other inlets 18b~ 20b of the air-flow dividing valves ll9~V836 18 and 20 are connected to the compre~sed gas source B
through a pressure regulator 23.
~ he pressure regulator 23 is in ~act an air reducing valve andicated at the same Ref.No.23 having a~y of the known constructions suitable for the purpose.
~ he other control chamber 16b of one of the two-position three-way control directional valves 16 i~ communicated9 thro-ugh one inlet 18a, 20a o~ one air-operated isolating valve 18, 20, with the outlet 15d of the two-position power di-rectional valve 15.-~ ne inlet~ l9a, 21a of the other air-operated isolating valves 19, 21 of the other two-position control directional valve 17 of each intensifier 1 are connected, via the direc-tional element 22 and the pressure reducer 23, to the com-pressed gas ~o~rce B.
~ he other inlets l9b, 21b thereof are connected to the air chamber 2 of the same inten~ifier 1 and to the outlets 15e of the power directional valves 15.
` ~-he other control chamber 17b of tho other three-~ay control directional valve 17 i3 communicated, through the other inlet~ 19b, 21b of the air-operated isolating valves 19, 21, through the outlet 15O of the power directional valve~ 15 thereof, with the compressed gas source B, or with the atmosphere.
~40836 ~ he outlet~ 18c, 19c, 20c, 21c of each o~ the air-operated valves 18, 19, 20, 21 are connected to the other control chamber ~6b, 17b o~ the control directional valves 16, 17 so as to ~witch over their inlets 16c, 17c and outlets 16d, 17d depending upon ~hether a pres~ure i5 present in ~he air chamber~ 2 o~ the intensifier 1.
~ he pneumohydraulic pumping tabion di~closed in the present invention operates as follow~
Upon putting the pumping ~tat1on in operation com-pressed gas is force-fed ~rom the source B to the inlets 15c o~ the two-position air-operated power directional valve~ 15, and further on through the ports thereof to the right-hand (as viewed in the drawing~ air chambers 2 of the intensifiers 1.
As it can be see~ ~rom the drawing the piston 4 of the left-hand intensifier 1 a~sume~ it~ rightmost po~ition, while the p~ston 4 of the right-hand intensifier 1 is in the leftmost position. The air pressure pulse (signal). i~
delivered ~rom the outlet 15e of the left-hand (as seen in the drawing~ two-position power directional valve 15 .
through the air-flow dividing valve 19 to the control chamber 17b of the other control air directional valve 17, thus switching it over to the position, wherein the control cha~ber 15b of the two-position power directional valve 15 (the right-hand one as seen .
., in the drawing) is communicated with the atmosphere.
As a re~ult, the air pressure pulse is delivered ~rom the outlet of the air pressure reducer valve 23 through the inlet 18b of the air-flow dividing valve 18 to the control chamber 16b o~ the two-position control air directional valve 16 to switch it over to the right-hand position, inas-much as its le~-hand control chamber 16a is communicated with the atmo~phere through the le~t-hand air chamber o~ the intensifier 1 and via the two-position power directional valve 15.
In this case the right-hand (as seen in the drawing) control chamber 15b of the two-position power dlrectional valve 15 (the right-hand as seen in the drawing) i9 commu-nicated with the atmosphere. Then the air pressure pulse is delivered ~rom the outlet 15e of the right-hand (as in the drawing) two-position power directional valve 15 through the inlet 21b of the air-flow dividing valve 21 to the chamber 17b of the other control air directional valve 17 to shift it to the rightmost position, inas~uch as the air pressure pulse arriving in the chamber 17a of the control air di-rectional valve 17 from the air chamber 2 of the right-hand (as in the drawing) intensifier 1 is applied to a ~maller effective area of the directional element (not shown) of the control chamber 17a. As a result the control chamber 15c ~ .
-1~4C~836 of the left-hand (as seen in the drawing) two-position power directional valve 15 is communicated with the atmosphere.
~hen the air pressure pulse is delivered from the outlet of the air pressure reducer valve 23 through the air-~low dividing valve 20 and the inlet 20b to the control chamber 16b of the right-hand (as in the drawing) control directional valve 16.
At the same time compressed gas is ~orce-fed from the air chamber 2 of the right-hand (as seen in the drawing) în-tensifier 1 to ths control chamber 16a o~ the samo directional valve, with the result that the right-ha~d (as seen in the drawing) control air directional valve 16 i3 shi~ted to the position, wherein an air pressure pulse appears at the out-let 16d thereof and i9 then delivered to the control chamber 15b of the left-hand (as seen in the drawing) two-position power directional valve 15, whereas its directional element remains in tho same position.
Thu~, the piston 4 of the right-~and (as seen in the drawing) intensifier 1 is kept in the leftmost position, whereas the piston 4 of the left-hand (as see~ in the drawing~
intensifier 1 starts travelling to the left, thereby dis-placing the hydraulic fluid from the left-hand hydraulic chamber 3 of the left-hand (as seen in the drawingj inten-si~ier 1 through the hydraulic check valve 8a of the left-hand , (as seen in the drawing) hydraulic bridge 7 to the pressure hydraulic line 5 and further on to the hydraulic actuator A.
The outflow of the hydraulic ~luid ~rom the hydraulic actuator A i8 effected through the hydraulic exhaust line 6 and Yurther on through the hydraulic check valve 8c of the left-hand (as seen in the drawing) hydraulic bride 7 to the right-hand hydraulic chamber 3 of the left-hand (as seen in the drawing) intensifier 1. As the piston 4 of the intensi-fier 1 passes on the right-hand control port 2b an air pres-sure pulse appears in the latter, which is then delivered to the control chamber 17a of the other control directional valve 17 (the left-hand one as seen in the drawing)~ which in this case remains in the right-hand position since an air pres~ure pulse appears in it3 control chamber 17b having a larger-area directional element (not shown), said air pres-sure pulse being sent from the outlet 15e of the left-hand (as seen in the drawing) two-position power directional valve 15.
As the pi~ton 4 of the intensifier 1 passes on the left-hand control port 2a of the intensifier 1, an air pressure pulse appears in the latter, which arrives then in the con-trol chamber }6a of the main control directional valve 16 (the left-hand one a~ seen in the drawing) and overcomes the force of pressure of compressed gas effective in the ~ .
: ; ' ~ ` , 114V83~
control chamber 16b, said gas being delivered from the air pres~ure reducing valve 23 through the port 18b of the air-flow dividing valve 18.
Thus, the control directional valve 16 i8 shifted to the left-hand (as seen in the drawing) position, and an air pressure pulse appears at the outlet 16d thereof, said pulse then arriving in the control chamber 15a of the right-hand (as seen in the drawing) two-position power directional valve 15 to shift the latter to the left-hand position.
Next, the piston 4 of the right-hand (as seen in the dra-wing) intensifier 1 starts travelling to the right, whereas the piston 4 of the left-hand (as seen in the drawing) intensifier 1 keeps travelling to the left.
As soon as the right-hand (as seen in the drawing) two-position power directional ~alve 15 is shifted to the left an air pressure pulse is delivered from its outlet 15d through the air-flow dividing valve 20 to the control chamber 16b of the main control air directional valve 16 to shift the latter to the position, wherein the control chamber 15b of the left-hand (as seen in the drawing) two-position power directional valve 15 is communicated with the atmosphere, whereby said directional valve is prepared for reversal.
In the course of joint tra~elling the piston 4 of the left-hand (as seen in the drawing) intensifier 1 come~ to ".
~.
114~836 the left-hand ~top ~not shown), whereas the pi8ton 4 of the other intensifier 1 passes on the left-hand control port 2a of the intensifier 1, In thi3 case the main control air directional valve 16 (the right-hand one as seen in the drawing) remain~ in the right-hand position, Next, the piston 4 of the right-hand (as seen in the drawing) intensifier 1 passes on the right-hand control port 2b, ~ he air pressure pulse appearing at the outlet of said port shïft~ the right-hand (as seen in the drawing) control air directional valve 17 to the position, wherein an air pres~ure pulse is delivered from its outlet 17d to the control chamber 15a of the left-hand (as seen in the drawing) two-position power directional valve, and compressed ~as fed from the source B is delivered from its outlet 15d to the air cham-ber 2 of the left-hand (as seen in the drawing) intensifier 1.
As a result the piston 4 of said inten~ifier 1 begins travelling to the right concurrently with the right-hand travel of the piston 4 of the other intensifier 1.
The balancing of the difference between the amount of the hydraulic fluid discharged into the pressure line 5 and that of said fluid returned to the exhaust line 6 is e~fected by the system, incorporating the bridges 7 of the hydraulic check valves 8, 9 and the flow equalizer 13 with the air pre~sure reducing valve 14.
.
' .
-. . .
.
~ ora~much a~ residual pre~ure in the air chambers 2 i~
blocked during each reversal of the inten~i~iers 1 by the pressure permanently admitted through the air pressure reducing valve 23 to the control chambers 16b, 17b of the control air directional valves 16, 17, no spurious air pressure signals and hence no false switching-over of the two-positional valves 15 occur.
The pilot mo~el of the proposed pneumodydraulic station has passed comprehensive tests that confirm high efficiency and reliability of the propo~ed pumping station.
Claims
1. A pneumohydraulic pumping station, comprising: a source of compressed gas; at least two double-action pneumo-hydraulic intensifiers variable-volume air chambers of each of said two double-action penumohydraulic intensifiers;
hydraulic chambers of each of said two double-action pneumohydraulic intensifiers being communicated, through hydraulic directional elements, with the pressure and exhaust lines to which actuators are connected; two-position power directional valves adapted to control the travel of the sliding member of one of said two double-action pneumohydraulic intensifiers in a preset concordance with the travel of the sliding member of the other of said double-action pneumohyd-raulic intensifiers said two-position power directional valves each having an inlet communicated with said source of compressed gas, an outlet communicated with the respective of said air chambers of said two double-action pneumohydraulic intensifiers, and two control chambers for switching over its inlet and outlet; two two-position control directional valves, each of them being adapted to shift the respective of said two-position power directional valves; another two two-posi-tion control directional valves adapted to shift said two-position power directional valves at a preset moment of the cycle; said two two-position control directional valves and said another two two-position control directional valves being in fact two-position three-way control directional valves with a two-end differential air piloting; two-position three-way control directional valves with two-end differen-tial air piloting each having an inlet, an outlet and two control chambers adapted to switch over said inlet and said outlet; one control chambers of each of the two-position three-way control directional valves with a two-end diffe-rential air piloting being adapted to periodically communicate, through one of said variable-volume air chambers of the res-pective one of said two double-action pneumohydraulic inten-sifiers, with the source of compressed gas or with the atmosphere; the inlet of each of the two-position three-way con-trol directional valves with a two-end differential air pi-loting, is communicated with said source of compressed gas;
the outlet of the two-position three-way control directional valves adapted to shift one of said two-position power di-rectional valves of one of said two double-action pneumohyd-raulic intensifiers being so connected to the control chamber of one of said two-position power directional valves of the other of said two double-action pneumohydraulic intensifiers as to alternately communicate the control chamber of the other of said two-position power directional valves of the other of said two pneumohydraulic intensifiers with said source of compressed gas and with the atmosphere;
aid-flow dividing valves, one for each two-position three-way control directional valves; the outlet of each of said air-flow dividing valves being connected to the other control chamber of each of the two-position three-way control direc-tional valves so as to switch over the inlet and oitlet there-of depending upon whether a pressure is effective in said variable-volume air chambers of the respective one of said two pneumohydraulic intensifiers; one inlet of one of said air-flow dividing valves of one of the two-position three-way control directional valves of each of said two double-action pneumohydraulic intensifiers being connected, through the directional element, to one of said variable-volume air chambers of the same of said two double-action pneumohydraulic intensi-riers, and to the outlet of one of said two-position power directional valves thereof; the other inlet of one of said air-flow dividing valves of one of the two-position three-way control directional valves of each of said two double-action pneumohydraulic intensifiers being connected to said source of compressed gas through the pressure reducer valve; the other control chamber of one of the two-position three-way control directional valves being communicated, through said on inlet of one of said air-flow dividing valves, with the outlet of one of said two-position power directional valves and with said source of compressed gas; one inlet of the other of said air-flow dividing valves of the other of the two-position three-way control directional valves of the same of said two double-action pneumohydraulic intensifiers being connected to said source of compressed gas through the directional element and the pressure reducer valve, the other inlet of said air-flow dividing valves of the other of the two-position three-way control directional valves of the same of said two double-action pneumohydraulic intensifiers being connected to one of said variable-volume air chambers thereof and to the outlet of one of said two-position power directional valves thereof, the other control chamber of the other of the two-position three-way control directional valves of the same of said two double-action pneumohydraulic intensifiers being communicated, through said other inlet of the other of said air-flow dividing valves, with the outlet of one of said two-position power directional valves and with said source of compressed gas or with the atmosphere.
hydraulic chambers of each of said two double-action pneumohydraulic intensifiers being communicated, through hydraulic directional elements, with the pressure and exhaust lines to which actuators are connected; two-position power directional valves adapted to control the travel of the sliding member of one of said two double-action pneumohydraulic intensifiers in a preset concordance with the travel of the sliding member of the other of said double-action pneumohyd-raulic intensifiers said two-position power directional valves each having an inlet communicated with said source of compressed gas, an outlet communicated with the respective of said air chambers of said two double-action pneumohydraulic intensifiers, and two control chambers for switching over its inlet and outlet; two two-position control directional valves, each of them being adapted to shift the respective of said two-position power directional valves; another two two-posi-tion control directional valves adapted to shift said two-position power directional valves at a preset moment of the cycle; said two two-position control directional valves and said another two two-position control directional valves being in fact two-position three-way control directional valves with a two-end differential air piloting; two-position three-way control directional valves with two-end differen-tial air piloting each having an inlet, an outlet and two control chambers adapted to switch over said inlet and said outlet; one control chambers of each of the two-position three-way control directional valves with a two-end diffe-rential air piloting being adapted to periodically communicate, through one of said variable-volume air chambers of the res-pective one of said two double-action pneumohydraulic inten-sifiers, with the source of compressed gas or with the atmosphere; the inlet of each of the two-position three-way con-trol directional valves with a two-end differential air pi-loting, is communicated with said source of compressed gas;
the outlet of the two-position three-way control directional valves adapted to shift one of said two-position power di-rectional valves of one of said two double-action pneumohyd-raulic intensifiers being so connected to the control chamber of one of said two-position power directional valves of the other of said two double-action pneumohydraulic intensifiers as to alternately communicate the control chamber of the other of said two-position power directional valves of the other of said two pneumohydraulic intensifiers with said source of compressed gas and with the atmosphere;
aid-flow dividing valves, one for each two-position three-way control directional valves; the outlet of each of said air-flow dividing valves being connected to the other control chamber of each of the two-position three-way control direc-tional valves so as to switch over the inlet and oitlet there-of depending upon whether a pressure is effective in said variable-volume air chambers of the respective one of said two pneumohydraulic intensifiers; one inlet of one of said air-flow dividing valves of one of the two-position three-way control directional valves of each of said two double-action pneumohydraulic intensifiers being connected, through the directional element, to one of said variable-volume air chambers of the same of said two double-action pneumohydraulic intensi-riers, and to the outlet of one of said two-position power directional valves thereof; the other inlet of one of said air-flow dividing valves of one of the two-position three-way control directional valves of each of said two double-action pneumohydraulic intensifiers being connected to said source of compressed gas through the pressure reducer valve; the other control chamber of one of the two-position three-way control directional valves being communicated, through said on inlet of one of said air-flow dividing valves, with the outlet of one of said two-position power directional valves and with said source of compressed gas; one inlet of the other of said air-flow dividing valves of the other of the two-position three-way control directional valves of the same of said two double-action pneumohydraulic intensifiers being connected to said source of compressed gas through the directional element and the pressure reducer valve, the other inlet of said air-flow dividing valves of the other of the two-position three-way control directional valves of the same of said two double-action pneumohydraulic intensifiers being connected to one of said variable-volume air chambers thereof and to the outlet of one of said two-position power directional valves thereof, the other control chamber of the other of the two-position three-way control directional valves of the same of said two double-action pneumohydraulic intensifiers being communicated, through said other inlet of the other of said air-flow dividing valves, with the outlet of one of said two-position power directional valves and with said source of compressed gas or with the atmosphere.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/SU1980/000028 WO1981002448A1 (en) | 1980-02-27 | 1980-02-27 | Hydro-pneumatic installation |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1140836A true CA1140836A (en) | 1983-02-08 |
Family
ID=21616592
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000357822A Expired CA1140836A (en) | 1980-02-27 | 1980-08-07 | Pneumohydraulic pumping station |
Country Status (6)
| Country | Link |
|---|---|
| JP (1) | JPS57500201A (en) |
| CA (1) | CA1140836A (en) |
| DE (1) | DE3050277C2 (en) |
| FR (1) | FR2492903A1 (en) |
| SE (1) | SE430096B (en) |
| WO (1) | WO1981002448A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10361619B4 (en) * | 2003-12-30 | 2006-08-31 | Joachim-Andreas Wozar | Hydraulic actuator |
| BR102013024307B1 (en) * | 2013-09-23 | 2022-03-29 | Drausuisse Brasil Comércio E Locação De Unidades Hidráulicas Inteligentes S.A. | Hydraulic pressure generating unit with pneumatic drive |
| CN111561434B (en) * | 2020-05-28 | 2024-08-16 | 滁州吉玻液压系统技术有限公司 | Balance type pneumatic hydraulic pump |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU524018A1 (en) * | 1974-09-04 | 1976-08-05 | Московский Ордена Ленина Авиационный Институт Им.Серго Орджоникидзе | Pneumatic or hydraulic return action |
| DE2538870A1 (en) * | 1974-09-04 | 1976-04-01 | Mo Aviacionnyj I Im Sergo Ords | PNEUMATIC-HYDRAULIC PUMP SYSTEM |
| US4004420A (en) * | 1975-09-26 | 1977-01-25 | Anatoly Nikolaevich Gavrilov | Hydropneumatic pumping arrangement |
-
1980
- 1980-02-27 DE DE3050277T patent/DE3050277C2/en not_active Expired
- 1980-02-27 JP JP55501137A patent/JPS57500201A/ja active Pending
- 1980-02-27 WO PCT/SU1980/000028 patent/WO1981002448A1/en active Application Filing
- 1980-08-07 CA CA000357822A patent/CA1140836A/en not_active Expired
- 1980-10-23 FR FR8022707A patent/FR2492903A1/en active Granted
-
1981
- 1981-10-23 SE SE8106274A patent/SE430096B/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| JPS57500201A (en) | 1982-02-04 |
| FR2492903B1 (en) | 1985-03-29 |
| SE430096B (en) | 1983-10-17 |
| WO1981002448A1 (en) | 1981-09-03 |
| FR2492903A1 (en) | 1982-04-30 |
| DE3050277C2 (en) | 1985-04-18 |
| DE3050277T1 (en) | 1982-04-15 |
| SE8106274L (en) | 1981-10-23 |
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