CA1302782C - Rotary pressure intensifier - Google Patents
Rotary pressure intensifierInfo
- Publication number
- CA1302782C CA1302782C CA000529732A CA529732A CA1302782C CA 1302782 C CA1302782 C CA 1302782C CA 000529732 A CA000529732 A CA 000529732A CA 529732 A CA529732 A CA 529732A CA 1302782 C CA1302782 C CA 1302782C
- Authority
- CA
- Canada
- Prior art keywords
- low pressure
- fluid
- piston
- high pressure
- pressure
- 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 - Fee Related
Links
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
- F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
- F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
- F04B9/111—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
- F04B9/1115—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members the movement of the pumping pistons in only one direction being obtained by a single-acting piston liquid motor, e.g. actuation in the other direction by spring means
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
A pressure intensifier for a fluid comprises at least three piston assemblies disposed along mutually parallel axes equiangularly disposed with respect to a central axis of the intensifier and radially equidistant therefrom.
Each piston assembly comprises at least one low pressure cylinder and at least one axially aligned and opposed high pressure cylinder. each high pressure piston being connected to the aligned low pressure piston for conjoint axial movement therewith. Fluid is supplied to the low pressure cylinders from a supply means and discharged to a discharge means through a low pressure valve means operatively coupled to the pistons of each assembly so as to be driven thereby. High pressure collector means.
usefully in the form of a closed circuit, are provided for receiving high pressure fluid from the high pressure cylinders.
A pressure intensifier for a fluid comprises at least three piston assemblies disposed along mutually parallel axes equiangularly disposed with respect to a central axis of the intensifier and radially equidistant therefrom.
Each piston assembly comprises at least one low pressure cylinder and at least one axially aligned and opposed high pressure cylinder. each high pressure piston being connected to the aligned low pressure piston for conjoint axial movement therewith. Fluid is supplied to the low pressure cylinders from a supply means and discharged to a discharge means through a low pressure valve means operatively coupled to the pistons of each assembly so as to be driven thereby. High pressure collector means.
usefully in the form of a closed circuit, are provided for receiving high pressure fluid from the high pressure cylinders.
Description
'l'he inv~ntion relates to a pressure intensifier ~or use in association with pressurized fluids. ~or intensi~Yin~ the pressure o~` a ~luid.
BA KGROUN OF T~_INVEI~rr10~
Devices are available for increasing ~luid and liquid pressures~ which are dependent on some ou-tside power source or motor. i.e.. pumps. compressors. etc.
Other forms of devices are directed to the intensi~ication of the pressure o~ a ~luid (e.~. liquid or lu ~aseous~ medium b~ utiliæin~ the Pressure of the medium as the power source. In theory this can be achleved simplY
b~ exchan~in~ or trans~ormin~ a ~iven volume of medium at a ~irst pressure. with a reduced volume o~ medium at an increased pressure. A portion of the volume of medium will thus become waste. A smaller volume of medium at the increased Pressure will then be obtained and utilized for whatever purpose it i0 requ1red. ~uch sYstems of~`er attractive possibilities, In manY instances. it is desirable to utilize a high pressure ~iet. for example. of water. for cleanin~.
cuttin~ pulverising and the like. However. in the great ma~iorit~ of cases~ the approach to producing such hi~h pressure ~iet has been to apply some ~orm of exterior power such as an electrical or other motor. and a pump.
These sYstems are there~ore relativelY
expensive. ln addition. in for example. a hi~h pressure , "
water ,iet powered bY an electrical pump~ rigid precautions are needed to ensure safet~ from electric shock. Complex continuous ~`low circulation sYstems are also required to ~ .
`~ ~U eliminate '`hammer" and turbulence.
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lior man~ reasorJs~ there~ore, it is desirable w~lere possible 1or a ~luid pressure intensitier -to ouerate ~rom the pressure of the ~luid medium. ln the pa~t. such pressure intensi~iers as have heen available were ~enerall~ based on some form of double actin~ pi5tOlI
desi~n However. such earlier desi~ns have ~enerally speakin~ been relativel~ costl~ and cumbersome. involvin~
numerous parts, and have also incorporated various inefficiencies, leadin~ to considerabls wastage in lu pressure and volume. One o~ the problems of earlier designs is the intermittent nature of the high pressure ~low. Piston t~pe intensifiers usually produce an intermittent flow in which the hi~h pressure is produced as a series of high pressure pulses. ~learlY. it is desirable to use multiple pistons and to operate them at a sut~icient spesd to smooth out these pulses as ~ar as P05Sible, ~ ne o~ the sources o~' ine~$`iciency in prior art desi~n is the power loss involved in returning each piston aXter its power stroke. It is desirable as far as possible to reduce this power 105s and also to render the return stroke o~ the piston as iar as possible free of interference or resistance ~ eciprocatin~ piston pumps and compressors are known to be relativel~ inefficient and their manu~acturing cost is relatively high. Maintenance costs can also be si~nificant. The use of connectin~ rods and bearin~s involves lar~e masses of metal reciprocatin~ to and fro with conse~uent losses. In addition. reciprocatin~
pistons o~ this t~pe produce pressure only on one half of the stroke~ the other hal~ being merel~ a dead movement ~or return. ~onsequentl~. the ~luid medium is sub,iected to pressure pulses, I'o overcome this. a pressure stora~e tank or accumulator is usuall~ provided to accumulate fluid under pressure. 'l'his still further increases the expense.
~ learly, it is desirable to provide a compress~r 'functionin~ without these disadvantages. and in which mechanical movement is reduced.
lU In ~eneral, the approach o~ the invention is to provide a pressure intensifier which utilizes the pressure o~ a fluid medium. i.e.~ air. water or a h~draulic fluid.
to either increase the pressure of the fluid medium (e.~..
the air. oil or water~. or which uses the pressure of one fluid medium to intensify the pressure of another fluid medium.
In either case, the general principles of the pressure intensifier mechanism are generallY similar. and the appearance is similAr.
M~o~X~ E~E ~ IQU
The invention seeks to overcome these t`oregoing disadvantages 'by the provision of a pressure intensifier ~`or a Xluid medium having at least three piston assemblies disposed along mutually parallel axes equian~ularlY
disposed with respect to a central axis o~' the intensifier and radially equidistant therefrom. Fluid is supplied to the low pressure cylinders from a supply means and discharged to a discharge means through a low pressure valve means operatively coupled to the pistons o~ the piston assem'blies so as to be driven b~ axial movement of , .
~30Z78Z
such pistons.
~ roadl~, an intensi~ier ~n accordance with this invention can. therefore~ be defined as comprisin~ at least three piston assemblies~ such piston assembl.ies being disposed alon~ mutually parallel axes eguiangularl~
disposed with respect to a central axis o the intensi~ier and radially eguidistant there~rom. each piston assembly comprising: la) at least one low pressure cylinder~ ¢b) at least one axia1ly ali~ned and opposed hi~h pressure lu cYlinder coaxially disposed with the low pressure cylinder. (c) a low pressure piston disposed within the low pressure cylinder ~or axial movement therein. and (d) a high pressure piston disposed within the high pressure cylinder for axial movement therein~ the hi~h pressure piston being connected to the low pressure piston ~or con,ioint axial movement therewith; (~) low pressure ~`luid supply means for the supplY of low pressure f luid to the low pressure cylinder o~ each piston assembly; ~3) low pressure fluid discharge means for the dischar~e of low ~U pressure rluid from the low pressure cylinder ot' each piston assembly: (4~ low pressure valve means coupled to the low pressure cylinder of each piston assembly and adapted to control the supply of low pressure fluid to the low pressure cylinder o~ each piston assembly from the low pressure fluid supply means and the dischar~e of low pressure ~luid from the low pressure cylinder of each ~ ` piston assembly to the low pressure fluid dischar~e means;
:' and ~51 hi~h pressure fluid collector means for receiving hi~h pressure fluid from the hi~h pressure cylinders.
Usefully~ the low pressure valve means is driven .~ .
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by a valve drive transmission means operatively lnterconnecting the pistons o~ the piston assemblies to such low pressure valve means. ln one embodimen-t. the valve means comprises a central rotarY valve sha~'t, with a rotar~ valve mounted on that shaft. Usefully. the valve drive transmission means comprises a swash p.late which en~ages the pistons.
- With such provision oX a swash plate. the valve means can alternativel~ 'be in the form o~ a ball connected lu to or Yorming part of the swash plate so as to be movable therewith and which is movably supported in a fixed cup formed in the intensifier. A supply passage and a plurality of transfer pass~ges communicating with respective ones o~` the low pressure cylirlders~ which passages open as ports ln such a cup~ are then provided ~or cooperation with reces~es formed in the sur~ace of the 'ball for permitting fluid transfer between respective pairs oX said ports during operation o~' the intensifier.
Usefully, each piston assembly of an intensifier ~U in accordance with this invention comprises a pair of axially aligned and opposed high pressure cylinders coaxially disposed with the low pressure cylinder and a pair of high pressure pistons disposed within respective ones oX the hi~h pressure cylinders for axial movement therein. each high pressure piston being connected to the low pressure piston for con~ioint axial movement therewith.
Other important features of the present invention relate to the design and construction of the high pressure collector means as well as to a construction 9~ in which the high pressure c~linders and the high ,-' pressuure fluid collector means comprises a clo.sed circuit.
In such an intensi~'ier in accordance with thi~
invention each piston assembly preferabl~ also comprises two low pressure cylinders with two low pressure pistons therein and such low pressure pistons of each piston assembly are connected to respective ones of the high pressure pistons of that piston assembly to provide first and second pairs of high pressure cylinders and pistons and low pressure cylinders and pistons. Linkage means are then provided between the first and second pairs of high and low pressure pistons in each assembly for transmitting axial movement therebetween~
In accordance with a particularly use~'ul ~eature o~ an such intensifier in accordance with this invention.
the hi~h pre~sure cylinders and the low pressure cylinders of each piston assembly are interconnected and the low pressure pistons are connected to the low pressure valve means by the valve drive transmission means so that. in each piston assembly. axial movement o~ the low pressure piston of one o~ the first and second pairs of cylinders and pistons is e~`fective through a respective one of the linkage means to cause axial movement of the high pressure ,' piston of the other of the ~`irst and second pairs o~
cylinders and pistons.
In one modification, the high pressure cylinders and the hi~h pressure fluid collector means form a closed circuit including pressure reaction means ~`or reaction to high pressure therein.
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' ~ In accordance with another uset'ul ~eature o~
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~ 6-this invention~ an inten.si~ier i5 construc-ted with a multi-section bodY so that the low pressure cylinders are located in a low pressure c~linder block portion and the high pressure cYlinders are located in a high pressure cylinder block portion. the intensifier also including spacer means extending between such low pressure and high pressure cylinder block portions.
The various Yeatures of novelty which characterize the invention are pointed out with ll) particularity in the claims annexed to and Yorming part o~
this disclosure. For a better understandin~ of the invention, its operating advantages and speci~ic obiects attained by its use. reference should be had to the accompanying drawings and the ~`ollowing description matter in which there are illustrated and described preferred embodiment~ of the invention.
BR~E ~ RIPT10~_OF T~E_n~L~
Figure 1 is an exploded perspective illustration oY a pressure intensifier according to the invention;
Fi~ure 2 is a sectional side elevation through the pressure intensifier of Figure 1 when assembled;
Figure 3 is an enlarged perspective oY a detail of E'igures 1 and ~ showing conduits in phantom. and partly cut away;
Figure 4 is an enlarged plan view oY Figure 3.
showing valves and conduits in phantom;
E'igure 6 is a perspective oY the rotary valvs and swash plate assembly;
E'igure ~ is a sectional elevation of a ~urther embodiment;
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- h'igure 'i is a cut-away ~erspective o~ a portion o$ ~:igure ~;
E`igure ~ is an illustration showing an alternative embodiment o-~ an intensi~ier in accordance with this invention and which comprises a combined swash plate and valve assembly;
Figure g is a fragmentary enlarged view of a -ball and cup valve arrangement Provided in the intensifier shown in Fi~ure 8;
lU Figure 10 is an illustration o~` the ball formin~
part of the 'ball and cup arrangement of Figure ~; and E`igure 11 is an underview o~ the cup ~`orming part of the ball and cup arrangement of E~igure ~.
~h' _IPT~ OF TH~_@~_ERR~D EMBODIM~NTS
'~e~ore descri'bing the construction of a pressure intensiiier of thls invention. it should be understood that what is described is suitab'le for use in a variety of dit'~'erent situations. E`or example. on a small scale. it may be used in domestic applications such as a bathraom or kitchen accessory or. on a slightly larger scale. as an outdoor attachment to a garden hose. In other circumstances, it may be used commercially, for example, to provide hydraulic power from a compressed air source or ; to provide a high pressure water cuttin~ Jet.
It will, therefore ! be appreciated that the invention is illustrated as a pressure intensi~ier per se.
ln use. it could be incorporated in some other article such as a hand-held water jet sprayer~ dishwasher~
bathroom appliance~ or the li'ke. as an integral component thereo~.
i~O2~82 ~ or the present purposes. however. ~or the description of this invention. no such appliance or o~her device is iLlustrated.
On the other hand. the device might be incorporate~ in a simple system of liquid supply arld outlet conduits, where the higher pressure liquid will be used somewhere downstream. in some other unrelated -equipment.
With re~'erence now to the drawings. it will be lu seen that the pre5sure intensifier shown in ~'igures 1 to b comprises a plurality. in this case, three. combined low and high pressure piston assemblies each of which is illustrated as 10a. 10b~ and 10c. In this description.
when a number of identical components are indicated by a numerical legend ~'ollowed by alphabetical su~fices~ such components will collectively be indicated by the same .Legend without such su~ices. For example. the piston assemblies 1~a. l~'b and l~c will be collectively referred to as assemblies 10.
~u Each low and hi~h pre~sure piston assembly comprises a relatively large diameter low pressure piston 12 and a relativelY small diameter high pressure piston 14. I'he two pistons 12 and 14 are connected together by a hi~h pressure piston rod extension 16.
In t'he embodiment illustrated. the high pressure piston 14 and the extension 1~ are integral structures formed with the same diameter and of the same piece of material. It will. howe~er. be appreciated that this is - not necessary for the purposes of the'invention.
~ ~u In each o~ the piston rod extensions 16~ there ~02782 is provided a bearing notch l8. ~or purposes to be described below.
'f'he intensitier comprises a low pressure cylinder body 2~. and a hi~h pressure cYlinder body ~2.
The low pressure cylinder body 20 comprises a plurality of. in this case. three. low pressure cylinders 24a, 24b and 24c. ~`ormed around the perimeter ot' a circle~ the centre of the circle being located along the mutual central axis ot' the bodies 20 and 22.
1~ The lower ends of the low pressure cylinders 24 are open and the upper ends o~ the cylinders 24 are closed by plug members 26. This arrangement is merely for the sake ot' simplicity and economy in t'abrication. The plug members 2ff are of reduced diameter so as to define an annular liquid t'low space therearound and are closed oft`
at their upper ends by means of closure discs ~.
In order to supply low pressure t'luid to the upper ends of cylinders 24 and thereby operate t'he low pressure pistons 12. there i.5 provided a rotary valve ~U assembly indicated generally as 30. The rotary valve assembly 30 is located within a central axial bore 32 formed in body 20. A low pressure fluid supply conduit 34 is t'ormed throu~h body 20 and communicates with bore 32.
Fluid may be supplied, for example~ through a supply hose t'ittin~ indicated generally as 36.
The valve assembly 30 will be seen to comprise a stem or shat't 38 o~ reduced diameter relative to bore 32.
A sealing collar 4~ closes off the lower re~ion of bore 32 t`rom access to low pressure t`luid. ~n annular valve neck 41 is formed integrall~ with shaft 38 spaced above collar ~' , -10-- - \
4u. An upper valve segment indicated ~enerally at 4~ is provided at the upper end o~' the neck 41. Upper valve se~ment 42 i5 divided b~ an axially extendin~ valve partition wall 43.
A lower semi-circular transverse wall 44 partially separates valve neck 41 from upper valve segment 4~. An upper semi-clrcular transverse wall 45 partially closes of~ the upper end of upper valve se~ment 42. Walls 44 and 45 are on diametrically opposite sides of segment 1~ 4~.
Yalve se~ment 4~ is t'urther provided with a fluid distribution face 46 and a ~luid election face 47.
which faces are on opposite sides of the partition wall 43.
As the valve assembly 30 rotates. flu1d is first o~' all received around the valve neak 41. then transferred to the distribution face 46~ and thus to the respective low pressure cylindqr 24 forcing the corresponding low pressure piston 12 to move axially downwardly. as viewed ~u in the drawing. When the low pressure pistons 12 move in the opposite direction. i.e., upwardly on the return stroke. fluid rom the low pressure cylinders 24 is then elected back to the valve assembly 30.
l'he upper end of bore 32 is open so that fluid , ~rom the valve ~'ace 4'7 can be e,~ected through. for ; example, low pressure fluid outlet fitting 32a (E'igure 2).
Bore 32 is provided with a plurality. in this '~; case three~ liquid supply and return ports 48. each port 48 communicatin~ ~rom upper valYe segment 42 with A
respective low pressure cylinder 24 adlacent the annular :~`
~, - space surrounding the plug member 2b.
~ low pressure ~luid trans~'er conduit 49 extends downwardly from the fluid supply conduit 34 for a reason yet to be described.
~ haft 38 is connected to a transmission device, in this case a swash plate shaft 50, extending downwardly through the lower end o~' bore 32. Sha~t 50 has an angled bushing portion 5~ carrying a rotary annular swash plate 54 (omitted from E'igure ~ wash plate 54 rides in the lu notches 18 formed in the piston rod extensions 16.
The high pressure cylinder body 22 is ~ormed of two separate body portions 60 and 62. This two-part construction ~'acilitates its manufacture and repair in the event of failure. It will also be understood that the hi~h pressure section o$' the intensifier is sub,1ect to considerable stresses during operation and is, therefore.
more susceptible to fa-tigue t'ailure. It is~ however, also possible to manufacture the body 22 as a single body.
Body portion 60 is a disc-like member of ~V relatively thin cross-section, and is formed with three high pressure cylinders 64, two of which 64a and 64b are shown in the drawings. These cylinders 64 are axially aligned with the respective ones of the low pressure ;' cylinders 24 so that the piston assemblies lO can be received in respective pairs of cylinders 24 and 64.
An axial opening 66 is provided in bodr portion 60 to receive the sha~t ~0. ~ylinders 64 are counterbored to provide recesses for seals 70 which are continuously engaged by the high pressure pistons 14 during operation of the intensifier.
~ low pressure conduit passa~e 72 ext~nds through body portion 60 ~or transfer o~ low pressure ~`luid in a manner to be described below.
High pressure cylinder body portion 62 is formed with high pressure cylinders 74a. 74b and 74c~ aligned with cylinders 64 and cylinders 24. Body 62 has an axial bearing opening '76 aligned with opening 66. Opening 76 receives bearing 78 on the lower end 68 of shaft 50.
A low pressure conduit passage 80 is formed 1~ through body 62. aligned with passage 72.
In order to distribute low pressure fluid, and to collect high pressure fluid. a collector and transfer plate 82 is provided beneath body 62. ~late 82 is provided with three high pressure ~'luid wells 84a. 84b.
and 84c which are axially aligned with respecti~e ones of the high pressure cylinders '74.
A low pressure distribution well 86 is formed ~Jigned with low pressure conduit passage 80. Wells 84 and 8~ are interconnected wit'h one another by a series of ~U drillings or conduits in the radial plane and as described below with reference to E'igures 3 and 4.
1'he wells 84a. 84b. and 84c are also connected by further drillings to respective high pressure outlet ; ' openings 88a. 88b and 88c. ~uitable one-way check valves to be descrl'bed 'below are incorporated in the plate 82 to control flow.
A high pressure fluid collector ring 90 fits around plate 82. Ring 90 is provided with an interior annular groove 92 and a single hi~h pressure outlet 94.
The bodY 20, body portions 60 and 62 ! transfer plate 8~ and collector ring 90 are held together b~
suitable bol-ts or clamps (not shown). -the details ot' which are omitted tor the sake o~ clarit~.
~ spacer ring Y~ is ~itted between body 2~ and body portion 6u. and encloses the space around SWASh plate b4. ln order to communicate low pressure fluid ~'rom body 2V to transfer plate 82. a low pressure pipe 98 is provided~ which is connected by any suitable means (not shown) to low pressure transfer conduit 49 in body 20. Low 1~ pressure pipe ~8 passes through the space enclosed by spacer ring ~6, and through passages 72 and 80. into well 86 in plate 8~.
As best shown in Fi~ure 3 and 4. plate 8~ is provided with low pressure drillings or conduits 1~0a.
lU~b. lOOc, each oY which is provided with a respeetive one-wa~ eheek valve 102a. 102b. lV2e Inot shown in E'i~ure 3).
'l'he wells 84a. 84b. 8~c are also provided with respeetive high pressure eonduits lV4a. lV4b. 104e. each o~' whieh contains a respective one-waY eheek valve 106a.
106b. 106e (not shown in Fi~ure 3).
Conduits 104 terminate at outlets 88. and deliver high pressure fluid to groove 92 and outlet 94.
In operation. low pressure ~luid is supplied through supply f'itting 3~ and eonduit 84 to the valve neek 41 in bore 32. ~imultaneously. low pressure fluid is also supplied via transfer eonduit 4~ and pipe 98 to distribution well 8~ in pla-te 82. This low pressure fluid will f'low from distribution well 8~ through eonduits 100 ~V and one way eheek valves 102 to the three hi~h pressure cylind~r wells ff4.
Low pressure ~`luid ~rom neck 41 will flow u~ to the distribution face 46 of valve ~egment 4~. lt will then t~l~w into whichever one o~ ports 48 is registering with face 46. Fluid will then apply pressure to the upper surtace o~ the respective piston 12. causing it to move downwardly, i.e.. toward the high pressure cylinder 64 and body 74.
As one o~` the hi~h pressure pistons 14 moves 1~ downwardl~ within a respective one o~ the high pressure cylinders 64-74. the fluid in that high pressure cYlinder will thereby be sub~iected to a pressure which is a multiple o~ the low pressure applied to the low pressure piston 1~ b~ the low pressure ~luid. The fluid in the high pressure cylinder will thus be subjected to a much higher pressure than that in the low pressure c~linder.
I'he seals 70 are ef~ective to minimize loss of high pressure fluid through the space between the high pressure pistons 14 and the cylinder bores 64.
~0 As such high pressure piston 14 continues to move downwardly. it will force the high pressure ~luid out of the respective high pressure outlet conduit 104 and through the respective one way check valve 106 into the collector groove 92 in the collector rin~ 9U.
As such hih piston 12 is ~orced downwardly by the low pressure ~luid. it will of course cause rotation o~ swash plate 54. thereby rotatin~ the shaft 38. and bringing the distribution face 46 into registration with a new one ot' the ports 48.
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~0 ~otation ot' the swash plate 54 will also cause ~:.
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~30Z782 one o$ the other piston assemblies lU to move upwardly, thereby e,iecting the low pressure ~luid ~'rom that low pre~sure cylinder ~4. The low pressure ~luid in that cylinder will then be e.iected through the respec-tive port 48 into registration with the e,iection face 4'1. ~'inally such ~'luid will pass out through outlet ~itting 32a.
Thus. so lon~ as low pressure fluid i5 con-tinuously supplied to the supply fitting 36. -the piston assemblies 10 will continue to reciprocate down and up, lu convertin~ a flow ot' low pressure t`luid of a predetermined volume into a flow of high pressure fluid o~ a much smaller volume.
The re,iected low pressure ~luid which is not transferred downwardly to the hi~h pressure cylinders. is merely allowed to run to waste.
~ learl~. many variations may be made in the arrangement oY the invention. While three pistons and c~linders are shown. it is obvious that there may be more pistons and cylinders~ i~ desired. The rotary valve mechanism as shown i5 simply one example of a suitable valve mechanism which may be used to distribute the low pressure fluid to and from the cylinders. Many other forms o~ valve mechanisms may be suitable. It will also be apparent that in this system already described. the same ~`1uid is used both on the low pressure side ~nd on the high pressure side. This may be suitable in many circumstances such as. ~'or example. in the generation o~` a high pressure water ~et from a lower pressure water source. 1'his may be suitable ror use in. r`Or exam~le. the bathroom or in the ~arden. or in many industrial or :
commercial applications where a simple high pre3sure water jet is required. It may also be suitable in hi~h pressure cutting ~iet applications.
~ owever. there are certain circumstance~ wher~
it is desirable to use two separate f.Luids. ln this case.
an entirely separate source o~ ~luid could be used ~or supplylng the high pressure cylinders through the well 86 and supply conduits 100. In this case. the low pressure pipe g8 would not be provided.
1~ Also~ in this case. all of the low pressure f1uid would be re,~ected throu~h the outle-t fit-ting 3~a.
Th1s would have certain advanta@es where it was desired or essential to keep the two fluids. namely the low presssure and high pressure f1uids. separate.
lt would also enable the use of compressed air as the low presstlre source and water or some other f1uid a~ the high pres~ure fluid.
In ~till other circumstance~, it may be desirable to provide for a completely sealed high presssure fluid system wherein there i5 no contact between the high pressure fluid and some other system to which the high pressure is to be applied.
This may be achieved by the embodiment of Figure 6 and 7. ln addition. this further embodiment has certain other advantages in that it provides ~or essentially a double-actin~ pumpin~ functlon. which ma~ be arran~ed to provide greater compactness and a greater high pressure flow rate or a larger number of pulses per unit of time ~` than the embodiment o~ Figures 1 to 5.
The principle of operation of this alternative ., .
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embodiment i9 essentia.Lly the same as that alread~
described. Thus it will be seen to comprise upper and lower pumping units generally indicated at 2~0 and ~02 respectively and which are essentially mirror images o~`
o~le another. Each of the units 200 and 20~ is provided with three low pressure cylinders 204 and three high pressure cylinders 206. which are provided with respective piston sets ~08. E~ch o these piston sets 208 comprises a low pressure piston 210 and a high pressure piston 212.
1~ The two piston sets 208 which are axially aligned with each other will be referred to as a piston assembly 198.
A central rotary valve sha~t 216 is mounted in bearin~s 218 and is rotated by means of swash plate 22~.
~wash plate 220 interengages with notches 221 formed in an intermediate connecting rod 222. lntermediate rod 22~
interconnects the two low pressure pistons 210. so that two piston sets 2~8 which are in ali~nment with one another also move in unison as a piston assembly 1~8.
~ onnectin~ rods 22~ are separate from low ~U pressure pistons ~1(). and are movable relative thereto to accommodate movement of the peripheral edge of swash plate 220 in the radial direction.
In order to supply low pressure t`luid to the low pressure cylinders 204. a pair of upper and lower valve assemblies 223 are mounted on the sha~t 216. and both are rotated in unison by swash plate 220. ~he valve assèmblies 223 are of somewhat similar design to the valve assembly shown in E'i~ure 1 and have inlet and outlet faces on opposite sides. Low pressure f1uid will be supplied to the valve assemblies 223 by annular supply channels 224~
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~' ' : ~ ` ' - , .
which are both supplied b~ a single .supply conduit 22b.
shown schematicall~. The annular channels 2~4 correspond to the valve neck 41 of E'igure l~ and supply fluid to the valve assemblies 223 around the Yull 360 de~rees o~
rotation .
'rransXer ports 2~6 connect with the low pressure cylinders 204. and outlet conduits 227 are provided for the discharge ot' low pressure Yluid.
The lower of the two valve assemblies 2~3 in l~ E'igure 6 is shown in the supply mode~ that is to say, with low pressure fluid flowing through the supply conduit 225, around the annular channel 224 and into the c~linder 204.
The upper valve in E'igure ~ is shown in the return or outlet mode. In this mode. Yluid is eJected throu~h the end of the valve upwardl~ into the outlet conduit 227.
'~'he upper and lower outlet conduits 227 are connected by a conduit 228.
'[t will be noted that, in this embod1ment. the two piston sets 208 are arranged in what may be called an ~U axially opposed ~'ashion. with the two low pressure pistons 21U facin~ toward one another and the two high pressure pistons 2l2 extending away Yrom the assembly at opposite ends thereof.
The hi~h pressure pistons 212 operate in cylinders 20~ which are connected by passa~ewa~s 230 to respective sealed bellows chambers 232 defined b~ bellows ' 234. The bellows 234 have piston heads 236 which may move to and Yro in chambers 236 in response to pulses oY high pressure from the cylinders 206 . The piston heads 236 are ~U connected throu~h passageways 238 by connecting rods 24U
to cam members 242. ~am members 242 are slidable a~ainst sprin~3s ~44~
Low pressure trans~`er passageways ~4~ connect outlet conduits 22'7 to passageways 238. ~heck ~alves 248 are located irl passa~eways 246 and valves 248 seat aga~ns-t cam members ~4~.
Valves 248 are opera~le to permit ~low of low pressure fluid into passagewa~s 238 to replenish any losses, when plun~er rods 240 retract due to f1uid 1~ leaka~e.
~crews 25U support cam members 242 in the desired positions in the passa~eways 238.
It will thus be observed that the hi~h pressure fluid sides of the system are essentiall~ closed sealed systems, so that high pressure pulses caused by high pressure Pistons 212 will cause the piston heads 236 to extend and retract within chambers 235.
Some other fluid such as. ~or example. oil or the like maD fill the chambers 235 around the outside of ~U the bellows 234. Such fluid ma~ enter the chambers 235 via supply conduit 252. transfer conduits 254 and check valves 25~.
~uch fluid maY exit from chambers 232 via one-wav out~low valves 258. which are connected b~ an outflow conduit shown schematicallY at 260~
It will thus be seen that the high pressure , r pulses created bY the six high pressure pistons 212~ are transferred via the bellows 234 and pistons 236 to another fluid. In this waY it is possible to use two di~ferent ; 3~ fluids in the system without them contactin~ each other.
, --~0--' ~' ~ '~ . ' ' ' ' ~ eferring now to E'i~ures 8 to 11 of the accompanYin~ drawin~s. it will be rloted that there is shown therein a pressure intensi~ier indicated ~enerally and schematicall~ at 300 and including. as did the inter-sifier shown in the Fi~ures 1 to 5. a plurality of pairs ol' opposed and co-axial low pressure and high pressure cylinders 302 and 304 respectively. onlY one such pair being shown in Figure 8 for the sake of simplicitY~
As will become apParent as the description herein l~ proceeds. the intensifier 3~0 will be considered a.s havin~
three such pairs of cylinders.
The low pressure cylinders 302 house pistons 306 while the high pressure cylinders 304 house pistons 308 of smaller radial dimensions. ~ther component parts of the intensifier 300 which are identical with those of the inten~i~ier shown in Figures 1 to 5 will be identified bY
the same le~ends.
'I'he pi~tO~ 306 and 308 of each pair are interconnected by a rod 310 which en~ages A swash plate ~o genera1ly indicated at 312. The swash plate 312 comprises a ball 914 which is movabl~ seated in opposed cups 316 and 318 ~ormed as fixed parts of the body of the intensifier 300. The ball 314 and the cup 31B cooperate so as to provide a low pres.sure fluid control valve in a manner yet to be described.
E`rom E'i~ures 8 and 9. it will be noted that the intensifier 300 is provided with f1uid conduits 320 and 322 which are open at ports 326 and 328 respectivelY in the cup 316. The conduit 320 is a low pressure fluid inlet passage through which low pressure fluid is supplied .
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from supply ~ittin~ 36 and suPp.L~ conduit 34. 'l'he conduits 3~;' provide low pressure ~luid trans~'er passages through which fluid is trans~erred to the pressure ends of the low pressure cylinders 3~2. It will be understood that a separRte low pressure ~luid trarls~ex conduit 32~ will be - provided t'or each one o~ the low pressure cylinders 3~.
For example, in the partlcular embodiment illustrated.
three such transfer conduits g22 are provided. conduits 822a and 32~b being shown in E'igures 8 and ~.
lv The positions and shapes o~ the sup:ply port 326 and of the three transfer ports 328a. 328b and 3~8c are shown in Fi~ure 11.
For a reason which will become apparent as the description herein proceeds. a low pressure dischar~e trans~'er passage ~34 is pro~ided for the discharge of the ~'luid from the space 336 within the spacer ring ~ to the axial bore 32.
~ eference will now be made to E'i~ures 9. 10 and 11 ~rom which it will be seen that the ball 314 is formed ~U in its surYace with two recesses 33~ and 338. On tilting of the swash plate 31~. the recess 336 is selecti~ely and sequentially operable to interconnect the fluid inlet passa~e 32~ with the ~luid transfer passa~es 322 50 as ..
sequentially to supply low pressure ~luid to the pressure ends of the low pressure cylinders 3~2. The annular ~ recess 338 is operable sequentially to be aligned with the : transfer passa~es 32~ so as to permit discharge of low pressure ~luid ~rom the low pressure cylinders 302 during the discharge strokes of the low pressure pistons~ Such ~U dischar~ed fluid ~lows through the recess 338 and into the : :
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space 33b containing the swash plate 312. so displacin~
~llaid ~rom that space throu~h the discharge transYer passage 334 and into the axial bore 3~.
It will be understood that such ~'low oY the low pressure fluid through the space within the spacer rin~ ~6 is possible and advanta~eous when the low pressure ~luid is a 1iguid. such as oil. which will then be effective to lubricate the moving parts o~ the intensi~`ier contained within that space 335. Obvious1y. where the low pressure 1~ ~luid is not a lubricant. the annular recess 338 would be positioned so as sequentially to permit the flow oY ~luid ~rom the low pressure cylinders 3~2 to a separate fluid dischar~s passage opening into the cup 316.
The ~oregoing is a description o~ preferred .embodiments of the invention which is given here by way of exampls only. The invention is not to be taken as limited to any ot the specific ~eatures as described. but comprehends all such variations thereof as come within the scope of the appended claims.
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BA KGROUN OF T~_INVEI~rr10~
Devices are available for increasing ~luid and liquid pressures~ which are dependent on some ou-tside power source or motor. i.e.. pumps. compressors. etc.
Other forms of devices are directed to the intensi~ication of the pressure o~ a ~luid (e.~. liquid or lu ~aseous~ medium b~ utiliæin~ the Pressure of the medium as the power source. In theory this can be achleved simplY
b~ exchan~in~ or trans~ormin~ a ~iven volume of medium at a ~irst pressure. with a reduced volume o~ medium at an increased pressure. A portion of the volume of medium will thus become waste. A smaller volume of medium at the increased Pressure will then be obtained and utilized for whatever purpose it i0 requ1red. ~uch sYstems of~`er attractive possibilities, In manY instances. it is desirable to utilize a high pressure ~iet. for example. of water. for cleanin~.
cuttin~ pulverising and the like. However. in the great ma~iorit~ of cases~ the approach to producing such hi~h pressure ~iet has been to apply some ~orm of exterior power such as an electrical or other motor. and a pump.
These sYstems are there~ore relativelY
expensive. ln addition. in for example. a hi~h pressure , "
water ,iet powered bY an electrical pump~ rigid precautions are needed to ensure safet~ from electric shock. Complex continuous ~`low circulation sYstems are also required to ~ .
`~ ~U eliminate '`hammer" and turbulence.
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lior man~ reasorJs~ there~ore, it is desirable w~lere possible 1or a ~luid pressure intensitier -to ouerate ~rom the pressure of the ~luid medium. ln the pa~t. such pressure intensi~iers as have heen available were ~enerall~ based on some form of double actin~ pi5tOlI
desi~n However. such earlier desi~ns have ~enerally speakin~ been relativel~ costl~ and cumbersome. involvin~
numerous parts, and have also incorporated various inefficiencies, leadin~ to considerabls wastage in lu pressure and volume. One o~ the problems of earlier designs is the intermittent nature of the high pressure ~low. Piston t~pe intensifiers usually produce an intermittent flow in which the hi~h pressure is produced as a series of high pressure pulses. ~learlY. it is desirable to use multiple pistons and to operate them at a sut~icient spesd to smooth out these pulses as ~ar as P05Sible, ~ ne o~ the sources o~' ine~$`iciency in prior art desi~n is the power loss involved in returning each piston aXter its power stroke. It is desirable as far as possible to reduce this power 105s and also to render the return stroke o~ the piston as iar as possible free of interference or resistance ~ eciprocatin~ piston pumps and compressors are known to be relativel~ inefficient and their manu~acturing cost is relatively high. Maintenance costs can also be si~nificant. The use of connectin~ rods and bearin~s involves lar~e masses of metal reciprocatin~ to and fro with conse~uent losses. In addition. reciprocatin~
pistons o~ this t~pe produce pressure only on one half of the stroke~ the other hal~ being merel~ a dead movement ~or return. ~onsequentl~. the ~luid medium is sub,iected to pressure pulses, I'o overcome this. a pressure stora~e tank or accumulator is usuall~ provided to accumulate fluid under pressure. 'l'his still further increases the expense.
~ learly, it is desirable to provide a compress~r 'functionin~ without these disadvantages. and in which mechanical movement is reduced.
lU In ~eneral, the approach o~ the invention is to provide a pressure intensifier which utilizes the pressure o~ a fluid medium. i.e.~ air. water or a h~draulic fluid.
to either increase the pressure of the fluid medium (e.~..
the air. oil or water~. or which uses the pressure of one fluid medium to intensify the pressure of another fluid medium.
In either case, the general principles of the pressure intensifier mechanism are generallY similar. and the appearance is similAr.
M~o~X~ E~E ~ IQU
The invention seeks to overcome these t`oregoing disadvantages 'by the provision of a pressure intensifier ~`or a Xluid medium having at least three piston assemblies disposed along mutually parallel axes equian~ularlY
disposed with respect to a central axis o~' the intensifier and radially equidistant therefrom. Fluid is supplied to the low pressure cylinders from a supply means and discharged to a discharge means through a low pressure valve means operatively coupled to the pistons o~ the piston assem'blies so as to be driven b~ axial movement of , .
~30Z78Z
such pistons.
~ roadl~, an intensi~ier ~n accordance with this invention can. therefore~ be defined as comprisin~ at least three piston assemblies~ such piston assembl.ies being disposed alon~ mutually parallel axes eguiangularl~
disposed with respect to a central axis o the intensi~ier and radially eguidistant there~rom. each piston assembly comprising: la) at least one low pressure cylinder~ ¢b) at least one axia1ly ali~ned and opposed hi~h pressure lu cYlinder coaxially disposed with the low pressure cylinder. (c) a low pressure piston disposed within the low pressure cylinder ~or axial movement therein. and (d) a high pressure piston disposed within the high pressure cylinder for axial movement therein~ the hi~h pressure piston being connected to the low pressure piston ~or con,ioint axial movement therewith; (~) low pressure ~`luid supply means for the supplY of low pressure f luid to the low pressure cylinder o~ each piston assembly; ~3) low pressure fluid discharge means for the dischar~e of low ~U pressure rluid from the low pressure cylinder ot' each piston assembly: (4~ low pressure valve means coupled to the low pressure cylinder of each piston assembly and adapted to control the supply of low pressure fluid to the low pressure cylinder o~ each piston assembly from the low pressure fluid supply means and the dischar~e of low pressure ~luid from the low pressure cylinder of each ~ ` piston assembly to the low pressure fluid dischar~e means;
:' and ~51 hi~h pressure fluid collector means for receiving hi~h pressure fluid from the hi~h pressure cylinders.
Usefully~ the low pressure valve means is driven .~ .
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by a valve drive transmission means operatively lnterconnecting the pistons o~ the piston assemblies to such low pressure valve means. ln one embodimen-t. the valve means comprises a central rotarY valve sha~'t, with a rotar~ valve mounted on that shaft. Usefully. the valve drive transmission means comprises a swash p.late which en~ages the pistons.
- With such provision oX a swash plate. the valve means can alternativel~ 'be in the form o~ a ball connected lu to or Yorming part of the swash plate so as to be movable therewith and which is movably supported in a fixed cup formed in the intensifier. A supply passage and a plurality of transfer pass~ges communicating with respective ones o~` the low pressure cylirlders~ which passages open as ports ln such a cup~ are then provided ~or cooperation with reces~es formed in the sur~ace of the 'ball for permitting fluid transfer between respective pairs oX said ports during operation o~' the intensifier.
Usefully, each piston assembly of an intensifier ~U in accordance with this invention comprises a pair of axially aligned and opposed high pressure cylinders coaxially disposed with the low pressure cylinder and a pair of high pressure pistons disposed within respective ones oX the hi~h pressure cylinders for axial movement therein. each high pressure piston being connected to the low pressure piston for con~ioint axial movement therewith.
Other important features of the present invention relate to the design and construction of the high pressure collector means as well as to a construction 9~ in which the high pressure c~linders and the high ,-' pressuure fluid collector means comprises a clo.sed circuit.
In such an intensi~'ier in accordance with thi~
invention each piston assembly preferabl~ also comprises two low pressure cylinders with two low pressure pistons therein and such low pressure pistons of each piston assembly are connected to respective ones of the high pressure pistons of that piston assembly to provide first and second pairs of high pressure cylinders and pistons and low pressure cylinders and pistons. Linkage means are then provided between the first and second pairs of high and low pressure pistons in each assembly for transmitting axial movement therebetween~
In accordance with a particularly use~'ul ~eature o~ an such intensifier in accordance with this invention.
the hi~h pre~sure cylinders and the low pressure cylinders of each piston assembly are interconnected and the low pressure pistons are connected to the low pressure valve means by the valve drive transmission means so that. in each piston assembly. axial movement o~ the low pressure piston of one o~ the first and second pairs of cylinders and pistons is e~`fective through a respective one of the linkage means to cause axial movement of the high pressure ,' piston of the other of the ~`irst and second pairs o~
cylinders and pistons.
In one modification, the high pressure cylinders and the hi~h pressure fluid collector means form a closed circuit including pressure reaction means ~`or reaction to high pressure therein.
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~ 6-this invention~ an inten.si~ier i5 construc-ted with a multi-section bodY so that the low pressure cylinders are located in a low pressure c~linder block portion and the high pressure cYlinders are located in a high pressure cylinder block portion. the intensifier also including spacer means extending between such low pressure and high pressure cylinder block portions.
The various Yeatures of novelty which characterize the invention are pointed out with ll) particularity in the claims annexed to and Yorming part o~
this disclosure. For a better understandin~ of the invention, its operating advantages and speci~ic obiects attained by its use. reference should be had to the accompanying drawings and the ~`ollowing description matter in which there are illustrated and described preferred embodiment~ of the invention.
BR~E ~ RIPT10~_OF T~E_n~L~
Figure 1 is an exploded perspective illustration oY a pressure intensifier according to the invention;
Fi~ure 2 is a sectional side elevation through the pressure intensifier of Figure 1 when assembled;
Figure 3 is an enlarged perspective oY a detail of E'igures 1 and ~ showing conduits in phantom. and partly cut away;
Figure 4 is an enlarged plan view oY Figure 3.
showing valves and conduits in phantom;
E'igure 6 is a perspective oY the rotary valvs and swash plate assembly;
E'igure ~ is a sectional elevation of a ~urther embodiment;
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- h'igure 'i is a cut-away ~erspective o~ a portion o$ ~:igure ~;
E`igure ~ is an illustration showing an alternative embodiment o-~ an intensi~ier in accordance with this invention and which comprises a combined swash plate and valve assembly;
Figure g is a fragmentary enlarged view of a -ball and cup valve arrangement Provided in the intensifier shown in Fi~ure 8;
lU Figure 10 is an illustration o~` the ball formin~
part of the 'ball and cup arrangement of Figure ~; and E`igure 11 is an underview o~ the cup ~`orming part of the ball and cup arrangement of E~igure ~.
~h' _IPT~ OF TH~_@~_ERR~D EMBODIM~NTS
'~e~ore descri'bing the construction of a pressure intensiiier of thls invention. it should be understood that what is described is suitab'le for use in a variety of dit'~'erent situations. E`or example. on a small scale. it may be used in domestic applications such as a bathraom or kitchen accessory or. on a slightly larger scale. as an outdoor attachment to a garden hose. In other circumstances, it may be used commercially, for example, to provide hydraulic power from a compressed air source or ; to provide a high pressure water cuttin~ Jet.
It will, therefore ! be appreciated that the invention is illustrated as a pressure intensi~ier per se.
ln use. it could be incorporated in some other article such as a hand-held water jet sprayer~ dishwasher~
bathroom appliance~ or the li'ke. as an integral component thereo~.
i~O2~82 ~ or the present purposes. however. ~or the description of this invention. no such appliance or o~her device is iLlustrated.
On the other hand. the device might be incorporate~ in a simple system of liquid supply arld outlet conduits, where the higher pressure liquid will be used somewhere downstream. in some other unrelated -equipment.
With re~'erence now to the drawings. it will be lu seen that the pre5sure intensifier shown in ~'igures 1 to b comprises a plurality. in this case, three. combined low and high pressure piston assemblies each of which is illustrated as 10a. 10b~ and 10c. In this description.
when a number of identical components are indicated by a numerical legend ~'ollowed by alphabetical su~fices~ such components will collectively be indicated by the same .Legend without such su~ices. For example. the piston assemblies 1~a. l~'b and l~c will be collectively referred to as assemblies 10.
~u Each low and hi~h pre~sure piston assembly comprises a relatively large diameter low pressure piston 12 and a relativelY small diameter high pressure piston 14. I'he two pistons 12 and 14 are connected together by a hi~h pressure piston rod extension 16.
In t'he embodiment illustrated. the high pressure piston 14 and the extension 1~ are integral structures formed with the same diameter and of the same piece of material. It will. howe~er. be appreciated that this is - not necessary for the purposes of the'invention.
~ ~u In each o~ the piston rod extensions 16~ there ~02782 is provided a bearing notch l8. ~or purposes to be described below.
'f'he intensitier comprises a low pressure cylinder body 2~. and a hi~h pressure cYlinder body ~2.
The low pressure cylinder body 20 comprises a plurality of. in this case. three. low pressure cylinders 24a, 24b and 24c. ~`ormed around the perimeter ot' a circle~ the centre of the circle being located along the mutual central axis ot' the bodies 20 and 22.
1~ The lower ends of the low pressure cylinders 24 are open and the upper ends o~ the cylinders 24 are closed by plug members 26. This arrangement is merely for the sake ot' simplicity and economy in t'abrication. The plug members 2ff are of reduced diameter so as to define an annular liquid t'low space therearound and are closed oft`
at their upper ends by means of closure discs ~.
In order to supply low pressure t'luid to the upper ends of cylinders 24 and thereby operate t'he low pressure pistons 12. there i.5 provided a rotary valve ~U assembly indicated generally as 30. The rotary valve assembly 30 is located within a central axial bore 32 formed in body 20. A low pressure fluid supply conduit 34 is t'ormed throu~h body 20 and communicates with bore 32.
Fluid may be supplied, for example~ through a supply hose t'ittin~ indicated generally as 36.
The valve assembly 30 will be seen to comprise a stem or shat't 38 o~ reduced diameter relative to bore 32.
A sealing collar 4~ closes off the lower re~ion of bore 32 t`rom access to low pressure t`luid. ~n annular valve neck 41 is formed integrall~ with shaft 38 spaced above collar ~' , -10-- - \
4u. An upper valve segment indicated ~enerally at 4~ is provided at the upper end o~' the neck 41. Upper valve se~ment 42 i5 divided b~ an axially extendin~ valve partition wall 43.
A lower semi-circular transverse wall 44 partially separates valve neck 41 from upper valve segment 4~. An upper semi-clrcular transverse wall 45 partially closes of~ the upper end of upper valve se~ment 42. Walls 44 and 45 are on diametrically opposite sides of segment 1~ 4~.
Yalve se~ment 4~ is t'urther provided with a fluid distribution face 46 and a ~luid election face 47.
which faces are on opposite sides of the partition wall 43.
As the valve assembly 30 rotates. flu1d is first o~' all received around the valve neak 41. then transferred to the distribution face 46~ and thus to the respective low pressure cylindqr 24 forcing the corresponding low pressure piston 12 to move axially downwardly. as viewed ~u in the drawing. When the low pressure pistons 12 move in the opposite direction. i.e., upwardly on the return stroke. fluid rom the low pressure cylinders 24 is then elected back to the valve assembly 30.
l'he upper end of bore 32 is open so that fluid , ~rom the valve ~'ace 4'7 can be e,~ected through. for ; example, low pressure fluid outlet fitting 32a (E'igure 2).
Bore 32 is provided with a plurality. in this '~; case three~ liquid supply and return ports 48. each port 48 communicatin~ ~rom upper valYe segment 42 with A
respective low pressure cylinder 24 adlacent the annular :~`
~, - space surrounding the plug member 2b.
~ low pressure ~luid trans~'er conduit 49 extends downwardly from the fluid supply conduit 34 for a reason yet to be described.
~ haft 38 is connected to a transmission device, in this case a swash plate shaft 50, extending downwardly through the lower end o~' bore 32. Sha~t 50 has an angled bushing portion 5~ carrying a rotary annular swash plate 54 (omitted from E'igure ~ wash plate 54 rides in the lu notches 18 formed in the piston rod extensions 16.
The high pressure cylinder body 22 is ~ormed of two separate body portions 60 and 62. This two-part construction ~'acilitates its manufacture and repair in the event of failure. It will also be understood that the hi~h pressure section o$' the intensifier is sub,1ect to considerable stresses during operation and is, therefore.
more susceptible to fa-tigue t'ailure. It is~ however, also possible to manufacture the body 22 as a single body.
Body portion 60 is a disc-like member of ~V relatively thin cross-section, and is formed with three high pressure cylinders 64, two of which 64a and 64b are shown in the drawings. These cylinders 64 are axially aligned with the respective ones of the low pressure ;' cylinders 24 so that the piston assemblies lO can be received in respective pairs of cylinders 24 and 64.
An axial opening 66 is provided in bodr portion 60 to receive the sha~t ~0. ~ylinders 64 are counterbored to provide recesses for seals 70 which are continuously engaged by the high pressure pistons 14 during operation of the intensifier.
~ low pressure conduit passa~e 72 ext~nds through body portion 60 ~or transfer o~ low pressure ~`luid in a manner to be described below.
High pressure cylinder body portion 62 is formed with high pressure cylinders 74a. 74b and 74c~ aligned with cylinders 64 and cylinders 24. Body 62 has an axial bearing opening '76 aligned with opening 66. Opening 76 receives bearing 78 on the lower end 68 of shaft 50.
A low pressure conduit passage 80 is formed 1~ through body 62. aligned with passage 72.
In order to distribute low pressure fluid, and to collect high pressure fluid. a collector and transfer plate 82 is provided beneath body 62. ~late 82 is provided with three high pressure ~'luid wells 84a. 84b.
and 84c which are axially aligned with respecti~e ones of the high pressure cylinders '74.
A low pressure distribution well 86 is formed ~Jigned with low pressure conduit passage 80. Wells 84 and 8~ are interconnected wit'h one another by a series of ~U drillings or conduits in the radial plane and as described below with reference to E'igures 3 and 4.
1'he wells 84a. 84b. and 84c are also connected by further drillings to respective high pressure outlet ; ' openings 88a. 88b and 88c. ~uitable one-way check valves to be descrl'bed 'below are incorporated in the plate 82 to control flow.
A high pressure fluid collector ring 90 fits around plate 82. Ring 90 is provided with an interior annular groove 92 and a single hi~h pressure outlet 94.
The bodY 20, body portions 60 and 62 ! transfer plate 8~ and collector ring 90 are held together b~
suitable bol-ts or clamps (not shown). -the details ot' which are omitted tor the sake o~ clarit~.
~ spacer ring Y~ is ~itted between body 2~ and body portion 6u. and encloses the space around SWASh plate b4. ln order to communicate low pressure fluid ~'rom body 2V to transfer plate 82. a low pressure pipe 98 is provided~ which is connected by any suitable means (not shown) to low pressure transfer conduit 49 in body 20. Low 1~ pressure pipe ~8 passes through the space enclosed by spacer ring ~6, and through passages 72 and 80. into well 86 in plate 8~.
As best shown in Fi~ure 3 and 4. plate 8~ is provided with low pressure drillings or conduits 1~0a.
lU~b. lOOc, each oY which is provided with a respeetive one-wa~ eheek valve 102a. 102b. lV2e Inot shown in E'i~ure 3).
'l'he wells 84a. 84b. 8~c are also provided with respeetive high pressure eonduits lV4a. lV4b. 104e. each o~' whieh contains a respective one-waY eheek valve 106a.
106b. 106e (not shown in Fi~ure 3).
Conduits 104 terminate at outlets 88. and deliver high pressure fluid to groove 92 and outlet 94.
In operation. low pressure ~luid is supplied through supply f'itting 3~ and eonduit 84 to the valve neek 41 in bore 32. ~imultaneously. low pressure fluid is also supplied via transfer eonduit 4~ and pipe 98 to distribution well 8~ in pla-te 82. This low pressure fluid will f'low from distribution well 8~ through eonduits 100 ~V and one way eheek valves 102 to the three hi~h pressure cylind~r wells ff4.
Low pressure ~`luid ~rom neck 41 will flow u~ to the distribution face 46 of valve ~egment 4~. lt will then t~l~w into whichever one o~ ports 48 is registering with face 46. Fluid will then apply pressure to the upper surtace o~ the respective piston 12. causing it to move downwardly, i.e.. toward the high pressure cylinder 64 and body 74.
As one o~` the hi~h pressure pistons 14 moves 1~ downwardl~ within a respective one o~ the high pressure cylinders 64-74. the fluid in that high pressure cYlinder will thereby be sub~iected to a pressure which is a multiple o~ the low pressure applied to the low pressure piston 1~ b~ the low pressure ~luid. The fluid in the high pressure cylinder will thus be subjected to a much higher pressure than that in the low pressure c~linder.
I'he seals 70 are ef~ective to minimize loss of high pressure fluid through the space between the high pressure pistons 14 and the cylinder bores 64.
~0 As such high pressure piston 14 continues to move downwardly. it will force the high pressure ~luid out of the respective high pressure outlet conduit 104 and through the respective one way check valve 106 into the collector groove 92 in the collector rin~ 9U.
As such hih piston 12 is ~orced downwardly by the low pressure ~luid. it will of course cause rotation o~ swash plate 54. thereby rotatin~ the shaft 38. and bringing the distribution face 46 into registration with a new one ot' the ports 48.
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~0 ~otation ot' the swash plate 54 will also cause ~:.
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~30Z782 one o$ the other piston assemblies lU to move upwardly, thereby e,iecting the low pressure ~luid ~'rom that low pre~sure cylinder ~4. The low pressure ~luid in that cylinder will then be e.iected through the respec-tive port 48 into registration with the e,iection face 4'1. ~'inally such ~'luid will pass out through outlet ~itting 32a.
Thus. so lon~ as low pressure fluid i5 con-tinuously supplied to the supply fitting 36. -the piston assemblies 10 will continue to reciprocate down and up, lu convertin~ a flow ot' low pressure t`luid of a predetermined volume into a flow of high pressure fluid o~ a much smaller volume.
The re,iected low pressure ~luid which is not transferred downwardly to the hi~h pressure cylinders. is merely allowed to run to waste.
~ learl~. many variations may be made in the arrangement oY the invention. While three pistons and c~linders are shown. it is obvious that there may be more pistons and cylinders~ i~ desired. The rotary valve mechanism as shown i5 simply one example of a suitable valve mechanism which may be used to distribute the low pressure fluid to and from the cylinders. Many other forms o~ valve mechanisms may be suitable. It will also be apparent that in this system already described. the same ~`1uid is used both on the low pressure side ~nd on the high pressure side. This may be suitable in many circumstances such as. ~'or example. in the generation o~` a high pressure water ~et from a lower pressure water source. 1'his may be suitable ror use in. r`Or exam~le. the bathroom or in the ~arden. or in many industrial or :
commercial applications where a simple high pre3sure water jet is required. It may also be suitable in hi~h pressure cutting ~iet applications.
~ owever. there are certain circumstance~ wher~
it is desirable to use two separate f.Luids. ln this case.
an entirely separate source o~ ~luid could be used ~or supplylng the high pressure cylinders through the well 86 and supply conduits 100. In this case. the low pressure pipe g8 would not be provided.
1~ Also~ in this case. all of the low pressure f1uid would be re,~ected throu~h the outle-t fit-ting 3~a.
Th1s would have certain advanta@es where it was desired or essential to keep the two fluids. namely the low presssure and high pressure f1uids. separate.
lt would also enable the use of compressed air as the low presstlre source and water or some other f1uid a~ the high pres~ure fluid.
In ~till other circumstance~, it may be desirable to provide for a completely sealed high presssure fluid system wherein there i5 no contact between the high pressure fluid and some other system to which the high pressure is to be applied.
This may be achieved by the embodiment of Figure 6 and 7. ln addition. this further embodiment has certain other advantages in that it provides ~or essentially a double-actin~ pumpin~ functlon. which ma~ be arran~ed to provide greater compactness and a greater high pressure flow rate or a larger number of pulses per unit of time ~` than the embodiment o~ Figures 1 to 5.
The principle of operation of this alternative ., .
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embodiment i9 essentia.Lly the same as that alread~
described. Thus it will be seen to comprise upper and lower pumping units generally indicated at 2~0 and ~02 respectively and which are essentially mirror images o~`
o~le another. Each of the units 200 and 20~ is provided with three low pressure cylinders 204 and three high pressure cylinders 206. which are provided with respective piston sets ~08. E~ch o these piston sets 208 comprises a low pressure piston 210 and a high pressure piston 212.
1~ The two piston sets 208 which are axially aligned with each other will be referred to as a piston assembly 198.
A central rotary valve sha~t 216 is mounted in bearin~s 218 and is rotated by means of swash plate 22~.
~wash plate 220 interengages with notches 221 formed in an intermediate connecting rod 222. lntermediate rod 22~
interconnects the two low pressure pistons 210. so that two piston sets 2~8 which are in ali~nment with one another also move in unison as a piston assembly 1~8.
~ onnectin~ rods 22~ are separate from low ~U pressure pistons ~1(). and are movable relative thereto to accommodate movement of the peripheral edge of swash plate 220 in the radial direction.
In order to supply low pressure t`luid to the low pressure cylinders 204. a pair of upper and lower valve assemblies 223 are mounted on the sha~t 216. and both are rotated in unison by swash plate 220. ~he valve assèmblies 223 are of somewhat similar design to the valve assembly shown in E'i~ure 1 and have inlet and outlet faces on opposite sides. Low pressure f1uid will be supplied to the valve assemblies 223 by annular supply channels 224~
.
~' ' : ~ ` ' - , .
which are both supplied b~ a single .supply conduit 22b.
shown schematicall~. The annular channels 2~4 correspond to the valve neck 41 of E'igure l~ and supply fluid to the valve assemblies 223 around the Yull 360 de~rees o~
rotation .
'rransXer ports 2~6 connect with the low pressure cylinders 204. and outlet conduits 227 are provided for the discharge ot' low pressure Yluid.
The lower of the two valve assemblies 2~3 in l~ E'igure 6 is shown in the supply mode~ that is to say, with low pressure fluid flowing through the supply conduit 225, around the annular channel 224 and into the c~linder 204.
The upper valve in E'igure ~ is shown in the return or outlet mode. In this mode. Yluid is eJected throu~h the end of the valve upwardl~ into the outlet conduit 227.
'~'he upper and lower outlet conduits 227 are connected by a conduit 228.
'[t will be noted that, in this embod1ment. the two piston sets 208 are arranged in what may be called an ~U axially opposed ~'ashion. with the two low pressure pistons 21U facin~ toward one another and the two high pressure pistons 2l2 extending away Yrom the assembly at opposite ends thereof.
The hi~h pressure pistons 212 operate in cylinders 20~ which are connected by passa~ewa~s 230 to respective sealed bellows chambers 232 defined b~ bellows ' 234. The bellows 234 have piston heads 236 which may move to and Yro in chambers 236 in response to pulses oY high pressure from the cylinders 206 . The piston heads 236 are ~U connected throu~h passageways 238 by connecting rods 24U
to cam members 242. ~am members 242 are slidable a~ainst sprin~3s ~44~
Low pressure trans~`er passageways ~4~ connect outlet conduits 22'7 to passageways 238. ~heck ~alves 248 are located irl passa~eways 246 and valves 248 seat aga~ns-t cam members ~4~.
Valves 248 are opera~le to permit ~low of low pressure fluid into passagewa~s 238 to replenish any losses, when plun~er rods 240 retract due to f1uid 1~ leaka~e.
~crews 25U support cam members 242 in the desired positions in the passa~eways 238.
It will thus be observed that the hi~h pressure fluid sides of the system are essentiall~ closed sealed systems, so that high pressure pulses caused by high pressure Pistons 212 will cause the piston heads 236 to extend and retract within chambers 235.
Some other fluid such as. ~or example. oil or the like maD fill the chambers 235 around the outside of ~U the bellows 234. Such fluid ma~ enter the chambers 235 via supply conduit 252. transfer conduits 254 and check valves 25~.
~uch fluid maY exit from chambers 232 via one-wav out~low valves 258. which are connected b~ an outflow conduit shown schematicallY at 260~
It will thus be seen that the high pressure , r pulses created bY the six high pressure pistons 212~ are transferred via the bellows 234 and pistons 236 to another fluid. In this waY it is possible to use two di~ferent ; 3~ fluids in the system without them contactin~ each other.
, --~0--' ~' ~ '~ . ' ' ' ' ~ eferring now to E'i~ures 8 to 11 of the accompanYin~ drawin~s. it will be rloted that there is shown therein a pressure intensi~ier indicated ~enerally and schematicall~ at 300 and including. as did the inter-sifier shown in the Fi~ures 1 to 5. a plurality of pairs ol' opposed and co-axial low pressure and high pressure cylinders 302 and 304 respectively. onlY one such pair being shown in Figure 8 for the sake of simplicitY~
As will become apParent as the description herein l~ proceeds. the intensifier 3~0 will be considered a.s havin~
three such pairs of cylinders.
The low pressure cylinders 302 house pistons 306 while the high pressure cylinders 304 house pistons 308 of smaller radial dimensions. ~ther component parts of the intensifier 300 which are identical with those of the inten~i~ier shown in Figures 1 to 5 will be identified bY
the same le~ends.
'I'he pi~tO~ 306 and 308 of each pair are interconnected by a rod 310 which en~ages A swash plate ~o genera1ly indicated at 312. The swash plate 312 comprises a ball 914 which is movabl~ seated in opposed cups 316 and 318 ~ormed as fixed parts of the body of the intensifier 300. The ball 314 and the cup 31B cooperate so as to provide a low pres.sure fluid control valve in a manner yet to be described.
E`rom E'i~ures 8 and 9. it will be noted that the intensifier 300 is provided with f1uid conduits 320 and 322 which are open at ports 326 and 328 respectivelY in the cup 316. The conduit 320 is a low pressure fluid inlet passage through which low pressure fluid is supplied .
.
: ~ `
from supply ~ittin~ 36 and suPp.L~ conduit 34. 'l'he conduits 3~;' provide low pressure ~luid trans~'er passages through which fluid is trans~erred to the pressure ends of the low pressure cylinders 3~2. It will be understood that a separRte low pressure ~luid trarls~ex conduit 32~ will be - provided t'or each one o~ the low pressure cylinders 3~.
For example, in the partlcular embodiment illustrated.
three such transfer conduits g22 are provided. conduits 822a and 32~b being shown in E'igures 8 and ~.
lv The positions and shapes o~ the sup:ply port 326 and of the three transfer ports 328a. 328b and 3~8c are shown in Fi~ure 11.
For a reason which will become apparent as the description herein proceeds. a low pressure dischar~e trans~'er passage ~34 is pro~ided for the discharge of the ~'luid from the space 336 within the spacer ring ~ to the axial bore 32.
~ eference will now be made to E'i~ures 9. 10 and 11 ~rom which it will be seen that the ball 314 is formed ~U in its surYace with two recesses 33~ and 338. On tilting of the swash plate 31~. the recess 336 is selecti~ely and sequentially operable to interconnect the fluid inlet passa~e 32~ with the ~luid transfer passa~es 322 50 as ..
sequentially to supply low pressure ~luid to the pressure ends of the low pressure cylinders 3~2. The annular ~ recess 338 is operable sequentially to be aligned with the : transfer passa~es 32~ so as to permit discharge of low pressure ~luid ~rom the low pressure cylinders 302 during the discharge strokes of the low pressure pistons~ Such ~U dischar~ed fluid ~lows through the recess 338 and into the : :
~ .
space 33b containing the swash plate 312. so displacin~
~llaid ~rom that space throu~h the discharge transYer passage 334 and into the axial bore 3~.
It will be understood that such ~'low oY the low pressure fluid through the space within the spacer rin~ ~6 is possible and advanta~eous when the low pressure ~luid is a 1iguid. such as oil. which will then be effective to lubricate the moving parts o~ the intensi~`ier contained within that space 335. Obvious1y. where the low pressure 1~ ~luid is not a lubricant. the annular recess 338 would be positioned so as sequentially to permit the flow oY ~luid ~rom the low pressure cylinders 3~2 to a separate fluid dischar~s passage opening into the cup 316.
The ~oregoing is a description o~ preferred .embodiments of the invention which is given here by way of exampls only. The invention is not to be taken as limited to any ot the specific ~eatures as described. but comprehends all such variations thereof as come within the scope of the appended claims.
.~ ~
. ~
.
g_ ..
Claims (13)
1. A pressure intensifier for a fluid medium and com-prising:
a stationary low pressure cylinder block portion defining two ends;
stationary high pressure cylinder block portions located at respective ends of said low pressure cylinder block;
at least three piston assemblies, said piston assem-blies being disposed along mutually parallel axes equiangularly disposed with respect to a central axis of said intensifier and radially equidistant therefrom, each said piston assembly comprising;
low pressure cylinder means in said low pressure cylinder block portion;
a pair of axially aligned and opposed high pressure cylinders coaxially disposed with said low pressure cylinder means in said high pressure cylinder block por-tions;
low pressure piston means disposed within said low pressure cylinder means for axial movement therein;
a pair of high pressure pistons disposed within res-pective ones of said high pressure cylinders for axial movement therein, each said pair of high pressure pistons being linked to said low pressure piston means for con-joint axial movement therewith;
low pressure fluid to said low pressure cylinder means of each said piston assembly;
low pressure fluid supply means for the supply of low pressure fluid to said low pressure cylinder means of each said piston assembly;
low pressure fluid discharge means for the discharge of low pressure fluid from said low pressure cylinder means of each said piston assembly;
movable low pressure valve means in said low pressure cylinder block portion and disposed along a central axis thereof within said mutually parallel axes of said piston assemblies, and being movable within said low pressure block portion, said valve means being coupled to said low pressure cylinder means of each said piston assembly and adapted to control the supply of low pressure fluid to said low pressure cylinder means of each said piston assembly from said low pressure fluid supply means and to control the discharge of low pressure fluid from said low pressure cylinder means of each said piston assembly to said low pressure fluid discharge means;
valve drive transmission means operatively coupled to each of said piston assemblies between said two high pressure pistons of each said piston assembly, and dis-posed within said mutually parallel axes of said piston assemblies whereby movement of said piston assemblies in response to supply of low pressure fluid will cause movement of said low pressure valve means, and simulta-neously synchronize movement of said piston assemblies;
high pressure fluid supply means for supplying fluid to said high pressure cylinders; and, high pressure fluid collector means for receiving high pressure fluid from said high pressure cylinders.
a stationary low pressure cylinder block portion defining two ends;
stationary high pressure cylinder block portions located at respective ends of said low pressure cylinder block;
at least three piston assemblies, said piston assem-blies being disposed along mutually parallel axes equiangularly disposed with respect to a central axis of said intensifier and radially equidistant therefrom, each said piston assembly comprising;
low pressure cylinder means in said low pressure cylinder block portion;
a pair of axially aligned and opposed high pressure cylinders coaxially disposed with said low pressure cylinder means in said high pressure cylinder block por-tions;
low pressure piston means disposed within said low pressure cylinder means for axial movement therein;
a pair of high pressure pistons disposed within res-pective ones of said high pressure cylinders for axial movement therein, each said pair of high pressure pistons being linked to said low pressure piston means for con-joint axial movement therewith;
low pressure fluid to said low pressure cylinder means of each said piston assembly;
low pressure fluid supply means for the supply of low pressure fluid to said low pressure cylinder means of each said piston assembly;
low pressure fluid discharge means for the discharge of low pressure fluid from said low pressure cylinder means of each said piston assembly;
movable low pressure valve means in said low pressure cylinder block portion and disposed along a central axis thereof within said mutually parallel axes of said piston assemblies, and being movable within said low pressure block portion, said valve means being coupled to said low pressure cylinder means of each said piston assembly and adapted to control the supply of low pressure fluid to said low pressure cylinder means of each said piston assembly from said low pressure fluid supply means and to control the discharge of low pressure fluid from said low pressure cylinder means of each said piston assembly to said low pressure fluid discharge means;
valve drive transmission means operatively coupled to each of said piston assemblies between said two high pressure pistons of each said piston assembly, and dis-posed within said mutually parallel axes of said piston assemblies whereby movement of said piston assemblies in response to supply of low pressure fluid will cause movement of said low pressure valve means, and simulta-neously synchronize movement of said piston assemblies;
high pressure fluid supply means for supplying fluid to said high pressure cylinders; and, high pressure fluid collector means for receiving high pressure fluid from said high pressure cylinders.
2. A pressure intensifier as claimed in claim 1 and in which said low pressure valve means comprises a central rotary valve shaft, a rotary valve on said shaft and operable to distribute fluid to respective low pressure cylinder means as it rotates, and a rotary drive device on said valve shaft, in driving engagement with said low and high pressure piston assemblies.
3. A pressure intensifier as claimed in claim 1 and which includes a fluid transfer passageway communicating between said low pressure fluid supply means and said high pressure fluid supply means, a plurality of high pressure fluid distribution passageways communicating from said high pressure fluid supply means to a respec-tive ones of said high pressure cylinders for supplying fluid thereto, and one-way flow valve means in said high pressure fluid distribution passageways.
4. A pressure intensifier as claimed in claim 1 in which each said piston assembly comprises a said low pressure piston means and cylinder having a predetermined first diameter, and said high pressure pistons and cylinders each having a predetermined diameter less than the diam-eter of said low pressure piston and cylinder means.
5. A pressure intensifier as claimed in claim 4 and in which said valve drive transmission means comprises a swash plate mechanism.
6. A pressure intensifier as claimed in claim 5, in which said swash plate mechanism comprises a swash plate mounted on an axial shaft of said intensifier and in which said low pressure valve means is mounted on said axial shaft and adapted to interconnect for fluid flow therebetween a fluid supply port and a fluid discharge port sequentially and alternately with a fluid transfer port for each of said low pressure cylinder means.
7. A pressure intensifier as claimed in claim 1 and in which said high pressure fluid collector means and said high pressure cylinders comprise a closed circuit for each said piston assembly including pressure reaction means for reaction to high pressure therein.
8. A pressure intensifier as claimed in claim 7 and in which said pressure reaction means comprises a bellows means forming a fluid tight barrier and disposed in a pump chamber for pumping a second fluid through said pump chamber.
9. A pressure intensifier as claimed in claim 8 and which comprises a passage interconnecting said low pres-sure fluid discharge means and said closed circuit and including a replenishment flow control valve for replen-ishing fluid in said closed circuit for fluid losses due to leakage.
10. A pressure intensifier as claimed in claim 9 and in which said bellows means is secured to a movable piston head carrying an actuating piston rod connected to said replenishment flow control valve for actuating that valve.
11. A pressure intensifier as claimed in claim 1 compri-sing a swash plate operatively interconnecting said pis-tons of said piston assemblies and comprising a ball con-nected to said swash plate and movably supported in a fixed cup formed in said intensifier and;
low pressure valve means comprising a low pressure fluid supply passage, and a plurality of low pressure transfer passages, said passages opening as ports in said fixed cup and said transfer passages communicating with respective ones of said low pressure cylinders, and recesses in the surface of said ball for permitting fluid transfer between respective pairs of said ports in said cup for controlling the supply of low pressure fluid to said low pressure cylinder of each said piston assembly from said low pressure fluid supply means and the dis-charge of low pressure fluid from said low pressure cyl-inder of each said piston assembly to said low pressure fluid discharge means.
low pressure valve means comprising a low pressure fluid supply passage, and a plurality of low pressure transfer passages, said passages opening as ports in said fixed cup and said transfer passages communicating with respective ones of said low pressure cylinders, and recesses in the surface of said ball for permitting fluid transfer between respective pairs of said ports in said cup for controlling the supply of low pressure fluid to said low pressure cylinder of each said piston assembly from said low pressure fluid supply means and the dis-charge of low pressure fluid from said low pressure cyl-inder of each said piston assembly to said low pressure fluid discharge means.
12. A pressure intensifier for a fluid medium and com-prising:
at least three piston assemblies, said piston assem-blies being disposed along mutually parallel axes equian-gularly disposed with respect to a central axis of said intensifier and radially equidistant therefrom, each said piston assembly comprising:
a pair of low pressure cylinder;
a pair of axially aligned and opposed high pressure cylinder coaxially disposed with said low pressure cylin-der;
a pair of low pressure piston disposed within said low pressure cylinder for axial movement therein; and a pair of high pressure piston disposed within said high pressure cylinder for axial movement therein, said high pressure piston being connected to said low pressure piston for conjoint axial movement therewith ;
low pressure fluid supply means for the supply of low pressure fluid to said low pressure cylinder of each said piston assembly;
low pressure fluid discharge means for the discharge of low pressure fluid from said low pressure cylinder of each said piston assembly;
low pressure valve means coupled to said low pressure cylinder of each said piston assembly and adapted to con-trol the supply of low pressure fluid to said low pres-sure cylinder of each said piston assembly from said low pressure fluid supply means and the discharge of low pressure fluid from said low pressure cylinders of each said piston assembly to said low pressure fluid discharge means ;
valve drive transmission means operatively coupled to each of said piston assemblies whereby movement of said piston assemblies in response to supply of low pressure fluid will cause movement of said low pressure valve means, and simultaneously synchronize movement of said piston assemblies;
high pressure fluid supply means for supplying fluid to said high pressure cylinders; and high pressure fluid collector means for receiving high pressure fluid from said high pressure cylinders.
at least three piston assemblies, said piston assem-blies being disposed along mutually parallel axes equian-gularly disposed with respect to a central axis of said intensifier and radially equidistant therefrom, each said piston assembly comprising:
a pair of low pressure cylinder;
a pair of axially aligned and opposed high pressure cylinder coaxially disposed with said low pressure cylin-der;
a pair of low pressure piston disposed within said low pressure cylinder for axial movement therein; and a pair of high pressure piston disposed within said high pressure cylinder for axial movement therein, said high pressure piston being connected to said low pressure piston for conjoint axial movement therewith ;
low pressure fluid supply means for the supply of low pressure fluid to said low pressure cylinder of each said piston assembly;
low pressure fluid discharge means for the discharge of low pressure fluid from said low pressure cylinder of each said piston assembly;
low pressure valve means coupled to said low pressure cylinder of each said piston assembly and adapted to con-trol the supply of low pressure fluid to said low pres-sure cylinder of each said piston assembly from said low pressure fluid supply means and the discharge of low pressure fluid from said low pressure cylinders of each said piston assembly to said low pressure fluid discharge means ;
valve drive transmission means operatively coupled to each of said piston assemblies whereby movement of said piston assemblies in response to supply of low pressure fluid will cause movement of said low pressure valve means, and simultaneously synchronize movement of said piston assemblies;
high pressure fluid supply means for supplying fluid to said high pressure cylinders; and high pressure fluid collector means for receiving high pressure fluid from said high pressure cylinders.
13. A pressure intensifier as claimed in claim 12 in which, in each said piston assembly, said high pressure cylinders and said low pressure cylinders are intercon-nected and in which said low pressure pistons are con-nected to said low pressure valve means by said valve drive transmission means so that, in each said piston assembly, axial movement of said low pressure piston of one of said first and second pairs of cylinders and pis-tons is effective through a respective one of said lin-kage means to cause axial movement of said high pressure piston of the other of said first and second pair of cylinders and pistons, and vice-versa.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US82991986A | 1986-02-18 | 1986-02-18 | |
| US829,919 | 1986-02-18 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1302782C true CA1302782C (en) | 1992-06-09 |
Family
ID=25255902
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000529732A Expired - Fee Related CA1302782C (en) | 1986-02-18 | 1987-02-13 | Rotary pressure intensifier |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0233771A3 (en) |
| JP (1) | JPS62240481A (en) |
| CA (1) | CA1302782C (en) |
| FI (1) | FI870673A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10216951A1 (en) * | 2002-04-17 | 2003-11-06 | Bosch Rexroth Ag | hydrotransformer |
| JP2019065799A (en) * | 2017-10-03 | 2019-04-25 | Smc株式会社 | Pressure intensifying device |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB767325A (en) * | 1953-07-15 | 1957-01-30 | Imo Industri Ab | Improvements in or relating to hydraulic pump systems |
| DE1135609B (en) * | 1960-09-29 | 1962-08-30 | Borsig Ag | High pressure piston compressor |
| FR1441747A (en) * | 1965-04-30 | 1966-06-10 | Pompes D K M Sa | Low and regular flow pumping device |
| DE3014552C2 (en) * | 1980-04-16 | 1986-06-26 | Paul 4740 Oelde Hammelmann | Hydraulic drive device for an axial piston pump |
| DE3101694A1 (en) * | 1981-01-21 | 1982-08-05 | Paul 4740 Oelde Hammelmann | Method and device of recovering energy in cyclic processes employing a gaseous or liquid pressurised medium |
| EP0085725B1 (en) * | 1982-02-05 | 1984-11-28 | Bran & Lübbe GmbH | Piston-driven diaphragm pump |
-
1987
- 1987-02-13 CA CA000529732A patent/CA1302782C/en not_active Expired - Fee Related
- 1987-02-17 EP EP87301327A patent/EP0233771A3/en not_active Withdrawn
- 1987-02-18 FI FI870673A patent/FI870673A/en not_active IP Right Cessation
- 1987-02-18 JP JP62035438A patent/JPS62240481A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| FI870673A0 (en) | 1987-02-18 |
| EP0233771A2 (en) | 1987-08-26 |
| EP0233771A3 (en) | 1989-03-08 |
| JPS62240481A (en) | 1987-10-21 |
| FI870673A (en) | 1987-08-19 |
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| MKLA | Lapsed |