BE670391A - - Google Patents

Description

  

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  "Hydrostatic machine with axial or radial pistons."
The main patent n PV 18.509, filed on September 30, 1965, relates to a hydrostatic machine with axial or radial pistons comprising a distributor glass which is prevented from rotating and on the active face of which, which includes the distributor openings, the face of which slides. sealing of a piston support in a hydraulic fluid-tight manner, the sealing face of the piston support and the active face of the distributor glass comprising parts thereof.

   withdrawal, notches, accumulator pockets or the like which form a hydraulic slug to which lubricating and discharging liquid can be supplied from parts of the machine through which the hydroaulic fluid passes for discharging and lubricating the superficial parts

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 EMI2.1
 them, sliding over each other, of the Ót1ohÓ1tÓ face of the piston back support and of the active surface of the ice
 EMI2.2
 dispenser, characterized in that in the sealing face of the piston back support a large number of short-length dispensing grooves are provided which are distributed in

          near annulaironont around the axis of rotation of this support and of which at least one, however preferably three, are connected directly and permanently, for the passage of the hydraulic fluid, by distributed distributing grooves
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 around the edge of the support:

   back pistons with a gap to nearly uniform louse and back intake holes with reduced section, with cylindras of said back udder support <on8 whereas, on the active face of the distributor valve, facing the face
 EMI2.4
 The tightness of the piston back support - except for the same peripheral zone as the distributing grooves - are provided a large number of aocumulatrioos pockets, distributed on a circumference, the distance of which goes in the direction of the periphery. and on either side of the plane of the dead points of the glass, we are talking about less than the length of the grooves distributed. \ 1'.rioos, duo so that, during the rotation of the support of the pistons, at the corners some pockets accanulatricos,

   which are located on either side of the plane of the dead spots $ but preferably all the pockets of each half of the
 EMI2.5
 distributor ice, are interconnected intermittently as well as with the inlet hole (s) which are located on each side for the passage of the hydraulic fluid so that a short circuit between the soft halves of the glaco distributor is ompôché,
Due to the fact that the distributor grooves and the
 EMI2.6
 intake holes, which lead directly to

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 EMI3.1
 in cos grooves ot oo = uxiiquont each with a cylinder of the piston support for the passage of the hydraulic fluid:

     
 EMI3.2
 are established on the rotating piston-back support, cos holes ot cos grooves execute, balancing the operation, a relative movement, corresponding to that of the piston-back support, with respect to the accumulatric pockets in the glass
 EMI3.3
 non-rotating dispenser. As a result, it is formed near each distributor groove which is connected by an inlet hole to a cylinder of the piston back support, in the joint which separates the active faces of said support and of said ice cream, a field of greasing or do discharge that turns
 EMI3.4
 on synchronism with the support on q, .. stion.

   In 10 cases where one provides by ozomplo three vdpartios distributor grooves on the support of the pistons ot -. V.-cord 6ce by dos intake holes with three cylinders evenly distributed around the periphery of said support, three lubrication fields or do unload therefore run continuously with this support. As each of these fields is connected directly, by the corresponding inlet hole, to a back cylinders distributed around the periphery of the support of the pistons for the pasaago of the hydraulic fluid, the lubricating or discharge liquid supplied to
 EMI3.5
 each distributor groove is subjected roughly to the mbmo prossion quo the hydraulic fluid which is in the oy-
 EMI3.6
 l3.ndre corresponding.

   For this reason, the inlet fluid pressure automatically adapts to the pressure each time with the sealing face of the piston back support.
 EMI3.7
 tight against the activo faco of the ice distributor next to the peripheral part of said support, due to the pressure
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 of the hydraulic fluid which reigns in the cylinders, The hydraulic discharge of the proscion, produced by the admitted lubricant is therefore a substance proportionnollo to the pressure of the fluid

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 hydraulic in the corresponding peripheral part of the support ot pistons with which this peripheral part is clamped against the glass.



   While for known hydraulic clamps, which have an annular throttle groove extending ¯) continuously in the peripheral direction, the uniformity of the lubrication, it is seen to unload the active faces do, the clamp , especially in the case of significant variations in the load, fall sharply to be desired,

   that the effect of the lubrication can be easily completely interrupted or at least considerably influenced by solid particles which get stuck in this groove and especially that the part of the hydraulic slider close to the plane of the dead points ot the suction side of the distributor ice is often supplied only in an insufficient way with the liquid lubricant ot of discharge, one obtains obligatorily ,, for the machine with axial or radial pistons, being the object of the main patent with the aid of the fields of Lubrication ot do discharge which rotate synchronously with the support of the pistons, uno uniform and efficient distribution of the lubricant on the peripheral parts,

   which normally are not greased and discharged or only insufficiently, of the crapaudine
In addition, the pressure in the rotary distributor grooves automatically adapts to the pressure which varies continuously in the corresponding cylinders of the back piston support causing the rotation of the same. To obtain this automatic adaptation of the hydraulic fluid pressure in the lubrication and discharge fields which rotate in synchronism with said support, no special control or adjustment devices must be used, nor any special adjustment devices.

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 EMI5.1
 tmaloguos billhooks by which loo froso do manufacture are increased and which risk being d4t4ns4,

   everything we marry- ooeoitnnt an overcoilanoe ot a continuous oÉboe% ion, On the contrary, it suffices to provide back oimploa ot open admission hole which, by one end, oommwùquont, do px3rdncv, dirvotvtvntp with a dietributrico groove then cudté other heavy oxtrdmï opens into a cylindroa back of the support.



  Laying the rolativo rotation between 10 auppbrt dos pistons ot la glaco dio% ributrifà, at least quolquoo- = ca dos pockets accunulatricoo do ladito glaoo, which are located on either side of the dead-point plan, but preferably all the said pockets of each half of the above ice cream, are intermittently connected ontro ollos by the rainu-
 EMI5.2
 distributors enü660B in the sealing face of the piston back support ot avoo the intake hole (s) which are located,
 EMI5.3
 each time, in this half of said glaco for the paasago of the hydraulic fluid ot a short circuit between the soft me-
 EMI5.4
 ice cream is excluded,

   lprèa a certain rotation rolativo 8uppémont1ro ontro 10 support ot the aforesaid glaoo, the connection for the passage of the hydraulic fluid is interrupted for
 EMI5.5
 To be restored again after a certain time 7v in this way we obtain, in very short periods which depend on the speed of the hydrostatic machine, on the number and dimensions,
 EMI5.6
 dispenser grooves and back pockets aooumulatricos soft Words added fluid
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 adjoining z, these, uno liaison for io passago / nyaram.iquo between at least some otp do preferably, all the pockets of each half of the ice cream dispenser,

   this bond being cneuito intact so that
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 do very short tomps the completion of the aforementioned pockets and back ruinnras is accelerated and then again delays. Do this

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 way one gets not only a fine doeanto or in rémittente of the lubricating liquid or. to unload the oro, the 8.u ... hydraulic dine, but we produce, have the entire peripheral length of ladi to 1,) ro.o.ud .:

  ! .ne, .. short intervals and in several places around its perimeter, an upward flow of 1 torna, ... tively accelerates and retards hydraulic fluid which prevents the formation of obstructions. and incrustations,
 EMI6.2
 The intensity of the p .. 'cdssa.ge can obviously be regulated in the manner desired in each case by the number and the dimensions of the pockets accwnulatricea of the distributor ice and the distributing grooves of the support of the pistons as well as the number of the holes admission.

   According to the main patent.) The number of these inlet holes should not be too small .. at least soft and preferably three or more - so that, despite the rotation of the lubrication or discharge fields, one is ensures that pressure distribution
 EMI6.3
 vari-: rOP fortonont no roo produce in the peripheral direction of the hydraulic slider.

   As a result of the intermittent acceleration and discoloration of the hydraulic fluid supplied to the hydraulic slider in several
 EMI6.4
 places distributed over its entire length, the pressure of 6raS- sage or dohrre that goes. each time, from the inlet hole which is on the discharge side to the suction side 4, all the load variations which occur and which have the effect of modifying the pressure in the cylinders in progress are reduced in accordance with:

  discharge without
 EMI6.5
 that there is a delay in time which has produced a noticeable value so that, even for large and abrupt variations in the load, too strong a formation of the film of liquid may be weakened in the seal between the piston support and the distributor ice

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 EMI7.1
 whereas the portoa by back leaks weigh to be maintained between economically bearable limits.



  By çontroe one obtains a sufficient lubrication and uno deohar6o for the majority of the loads which can present parts of the surfaces which slide the one on the other
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 dîstributrica ice ot support for pedestrians. 00mm0
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 the hydraulic fluid always travels .pendant little. do tompu soft mote adding pochoo maïa to pou preo Dioultun6uont the whole / of the cbtd do retou-
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 moment or side of suction or return of the slider.

   hydraulic and everything has, t Mins a large part of the accumulatrïcoo pockets established in cos quoted, a healthy quantity of lubricating and discharging liquid is present in the aforesaid seal, so that it will generate a metal on metal oontaot of the surfaces which slide the unos on the others
 EMI7.5
 or an overheating to which collas is avoided,
Although the parts of the surface of the distribution ice which are found near the plane of the dead points
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 are constantly and sufficiently supplied with lubricating and discharge liquid, it is impossible, by the arrangement proposed in the invention, of the intake holes
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 zion, back dispenser grooves and back pochoo.acc = ulatrî- these,

   that a dirooto link is established on the aocumulatric pockets which are located on either side of the dead end plane, so that a diroot balancing of the soft back proosiona obtained from the Glaco is avoided with absolute certainty, By The pumping of lubricating and discharging liquid by pulsations of short duration avoids the possible formation of
 EMI7.8
 do deposits and inlays in the distributing grooves, in the ontrdoo and outlets of the intake holes or in the accumulating pockets where the solids are between

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 EMI8.1
 born by said liquid, so that the crapaudine, described, J / 1 in the main patent, is cleaned automatically, '
 EMI8.2
 In the pockets of alaço is formed,

   when shorting several or all of the pockets which find dead points on either side of the plane and with the aid of distributing grooves, a pressure whose size is approximately proportional to the product of the surface of the pocket ot the momentary pressure of the hydraulic fluid.
 EMI8.3
 than.

   Cotte pressure acit in antagonism with the foroo oxorode by the back support pistons (cylinder drum) on the distributor ice ot adjusts the tightening between the sliding faces los one on the other. This pressure determines the thickness of the film of the lubricant and the filler liquid, so that the formation and determination of the pressure is of particular importance for the smooth running of the machine.



   The axial or radial piston machine, which is the subject of the chief marshal, has the advantage that the unloading forces which automatically adapt to the momentary load of the machine can be determined by calculation with absolutely sufficient accuracy. for practice and in a significantly easier and simpler manner than for known embodiments, so that the dimensions
 EMI8.4
 the most advantageous for the conditions to be fulfilled can wax- obtained both for the distributrioos grooves
 EMI8.5
 quo for acounulatricoa pockets without significant testing.



  Another advantage of the hydrostatic machine, being the subject of the main patent, is that the active face of the craraudinc can be absolutely free of choke rains, inlet channels and orifio00 gauges. , because it suffices to make him include back poohos accumulators 1

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 which can be foreclosed easily by milling or. drilling of the active face of the ice using a bur or a suitable drill.

   The manufacture of the glass is therefore appreciably simpler and more economical than for the known embodiments for which this active face comprises grooves or throttling channels and intake holes which are often made up and arranged in 'in a complicated way.



   In cases where the distributing grooves formed in the sealing face of the piston back support ot the accumulator pockets provided for a bearing face of the distributing lens have preferably equal dimensions ontrol and are fixed, preferably on the primitive matme corocle more or less concontric to the axis of rotation, according to another characteristic of the main patent, the length of said grooves is given,

     measured in the peripheral direction of said support has a value nearly equal but preferably smaller than the gap between the pockets provided on the suction or return side or on the ice discharge side. In this way it is certain that, during the rotation of said support, all the pockets of each half of the ice are, for so long, connected ontro ollos by the distributing grooves for the passage of the hydraulic fluid so that all The pockets which are to be found on both sides of the plane of the dead points of the ice, are continuously mounted and during the course of their time through which the hydraulic fluid discharged from the loo intake holes passes.



   For an embodiment according to the main patent, the free soction closed distributing grooves has a value almost soft to four times greater than the section.

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 narrowest transverse back intake holes.

   We obtain
 EMI10.1
 as well as the hyèrnuliquo fluid, discharged into the ten-tributricose grooves, undergoes in these grooves a zero constriction or. notablot poino do sort quo, mtmo for back large variations in load or flow of hydraulic fluid, the pressures
 EMI10.2
 do co fluido, delivered by the inlet hole, are balanced in the position in which the grooves connect ontro them, for the passage of the hydraulic fluid the pockets which are located on either side of the plane of the dead points, then quo over all the length of the cake don soft halves of the roano ice each time a pressure for the lubricating liquid ot do
 EMI10.3
 discharge which practically corresponds,

   the pressure nonontanò on the side of the rofoulouont or on the side of the suction or of the rotation of the hydrostatic machine.



   To this offct we give the intake holes, which preferably parallel to the axis of rotation of the back support
 EMI10.4
 pistons, a diameter of about 1.18 to 1.18 mm, while the grooves of butxiao have in plane of the face of said support a width of about 15 to 3 and a depth of 'about 1.5 to 6 mm.



   Other characteristics of the subject of the patent
 EMI10.5
 main reside in the fact that, for a zucouvromont Io greatest possible entered the terminal parts don rai- nuros dietributriocc ot soft neighboring aoouciulatrioos pockets, los openings ontro cases terminal parts ot the neighboring pockets have back dimensions tnl-lomont grandos quai loro of the transfer of the hydraulic fluid contained in the aforesaid grooves, there is no or insignificant throttling offot.
 EMI10.6
 



  Do more, the dcartoment between los pochoolà the place, where. no found 10 .plan dos dead points of the g7.aao est "

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 significantly greater than the length of the back grooves distribu-
 EMI11.1
 knitting this decartomant removing about 7 to 20% greater than this length,
While the machinos with axial and radial pistons, formed as in the main brovot, gave allo
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 satisfaction we operate at uno vitosso rclativonont constant and, on pluo, éicv6o, we have observed that in the machinas do co genre, whose speed undergoes variations
 EMI11.3
 Importantly, especially with hydrostatic motors at very veriable speed, certain difficulties may be encountered which result in substance from the following causo.

   
 EMI11.4
 To ensure a sufficient seal on the distributor slaoo and the sealing ability of the piston support and to keep losses due to leaks at a value. reduced, the glass must be clamped with a corresponding great force against said support.

   For this offot, we use. cos prossours pistons or the like, stressed by pressure.
 EMI11.5
 of the hydraulic fluid which prevails from the delivery obt6 of the machine, so that the oxorodo clamping pressure on the delivery side of the Ice automatically adapts to the momentary pressure existing on the delivery side of the machine,
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 The clamping pressure. oxorc6o by pedestrians walking on the ice cream must be chosen large enough to quoym6m.0 for the greatest pressure of discharge produced in
 EMI11.7
 the seal between the distributor Claec and the sealing facci of the support of the pistons, a detachment of the ladito Glaoo from before the said face can not occur and that the ports by.

   leaks continued at reduced dtroon. The corrago force initiated on the ice must therefore be greater than the greatest force that can be produced in the aforementioned seal by curing the introduction of the lubricating liquid.

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 and therefore discharge, this dornière force acting in reverse with respect to the first.



   If one uses, in accordance with one embodiment of the main brovet, back dispenser grooves which have a significantly larger cross section, for example soft to four times as large, than glue back holes, it so produces at each connection between the accumulator pockets by ion distributing grooves a pressure of the hydraulic fluid, on the delivery side of the ice, which corresponds practically to the pressure with which the hydrostatic machine is operating at that moment, this pressure practically becoming equal to zero when it is produced onsuito uno separation, waterproof to hydraulic fluid, between the pockets,

   When the hydrostatic machine is operating at a relatively high speed, the pressures, which occur on the discharge side of the ice and which succeed at very short time intervals, add up to form an average pressure which is found. except in the middle of the machine the operating pressure of the machine is zero.



   The force which produces the clamping of the glass against the sealing faoe of the piston support can be chosen in such a way that it corresponds to this average pressure produced in the aforesaid seal. In this case, no excessive ports are formed by leaks in the seal of the hydraulic crapaudino ot one does not have to fear a seizure on the surfaces which slide the units on the others of the said crapaudine as a result of sorrage. too intense of the ice, On the other hand, if the hydrostatic machine turns at a relatively low speed, as often happens with hydrostatic motors with adjustable speed, it forms,

   for co-embodiment of the main patent,

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 relatively large variations are not always pronounced in the pressure in the joint of the crapaudine, because the pressure, at the moment when the proooion on the different distrious grooves or the accumulated pockets of the crapaudine have intorrupted, suddenly drops to zero, also on the side. discharge of the crapaudino, while it also suddenly breaks up to the momentary operating pressure of the hydrostatic machine as soon as the connection on the pockets and the loo grooves is re-established.



   To avoid, at such a reduced speed, too intense a detachment of the glass from the sealing face of the piston support, the clamping pressure, oxidized on the glass, must be maintained high enough so that ollo can balance the opposing force produced during the establishment of the connection for the passage of hydraulic fluid on the accumulator pockets and the distribution grooves of the hydraulic crapaudino.

   This means, however, at the moment when this bond is broken, that the glass has tightened with a very strong resultant force against the sealing face of the aforesaid support, which, as the pressure of the lubricating film and of the discharge is at the same time. which has become practically reduced to zero, to give rise to metal-to-metal contact between the parts of the surfaces, which sliding over each other, causing the hydraulic slider to heat up, or even seize, of these surfaces.



   To avoid these difficulties, the hydrostatic machine with axial or radial pistons, which is the subject of the main discussion, is improved, in accordance with the invention, in such a way that, while retaining the arrangement and the

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 EMI14.1
 oons'c.t.'cu'cion teenagers distributing grooves and back pO100 accu- mulatrieea provided respectively on the active face of the and distributrico / attr glass the sealing face of the piston back support by constituting said grooves as back sections
 EMI14.2
 do otranGlon grooves are given a free cross section noticeably smaller than the smaller cross section of the intake holes. We obtain
 EMI14.3
 so 5.avanto,

  a quopclanj3 the case where so produces a connection for the passage of the hydraulic fluid between the pockets of the ice $ it is formed, by the portions of throat grooves.
 EMI14.4
 Glomont provided on the sealing face of the aforesaid support a significant pressure drop starting from the inlet hole or holes which are at this moment on the delivery side of the ice to the plane of the dead points of said glass.

   At this time the pressure of the hydraulic fluid, on the discharge side of the hydraulic slider, is notably lower than the momentary operating pressure so that the
 EMI14.5
 The total force which tends to move the ice away from the sealing face of the piston is notably less than that which occurs when recourse is had to distributing grooves which have a large transverse cross section like C 01100 of the corresponding embodiment described in the main patent. This significantly lower average pressure of the lubricating film and discharge is primarily the cause that the port leaks are considerably smaller than those produced with the above embodiment of the main patent.

   Another important advantage is that the force which clamps the glass against the sealing face
 EMI14.6
 of the support of the pistons can ttro maintained at a value notably more potito quo for the aforementioned mode of realization

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 of the main patent because the maximal force, which cuts to the extent of the galce of the sealing face of said support, is notably smaller, for example by about half, which sticks in
 EMI15.1
 torvonant in the modo do above.

   Oe01 has, therefore its cbtdt for offot, uo the forao which sorya the, ice against the face of the etanohéi ty of the support d3S pedestrians ost tollociont weak quo mômo when it is produced a relative movement trbe slow ontro said support ot said glaco ot when pressure
 EMI15.2
 in the joint of the hydraulic cmpaudmo drops to zero (by interrupting the connection between the pockets and the sections of the throttle grooves), the surfaces of the slider which slide together are not liable to heat up or even seize up.

   In addition, the variations
 EMI15.3
 pressure between the maximum value @@ and the minimum value of the uncharging pressure 60 in the joint of the hydraulic valve block ot, consequently, the variations in pressure lead to the maximum value and the minimum value of the resolving do
 EMI15.4
 the pressure do corrago ot of the prosoion do ddeharac have a word added more
 EMI15.5
 notably / weakly, by cxcmplo of about half quo in the aforementioned embodiment of the main patent, do oorto
 EMI15.6
 although the hydrostatic machine forming the subject of the present invention, has a much more uniform narclio, rtx7.iro and less noisy, DODO with very weak vitossos.

   The conatitu.-
 EMI15.7
 tion of the hydraulic slider, which is the subject of the invention, is also very advantageous for hydrostatic machines with particularly large dimensions and for those operating at high rotating pressures for which the use of distributor grooves having a relatively large cross section to give the
 EMI15.8
 on the one hand, to larger ports by dos fuitoa oti d '

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 EMI16.1
 on the other hand, a 6th year of Voiro with a seizure at back speeds partieul1oromont reduced. tzar the altornéos accelerations and decelerations.

   of the current of the hydraulic fluid which are produced, to do 'short intorvalloo do tompo on various undrits of the perimeter onep0ahc also avoo ao greato certainty $ n8tào when the grooves of the tranalornont have a sootion rolativomcnt tr01to the formation of obstructions or i1Wruatatiôps, As on outro the fields of araiesago or do ddohargop whose pressure goes on dininuating from the inlet or the hole to the don pointa dead plane of the dispensing ice turn on eynclu'onisno with 10 support back pistons in relation to 4 the glaoo non rota .- 'ivo and oommo the pressure of the hydraulic fluid varies continuously in the intake holes and in the sections of the throttle grooves, rolié to cos holes for the passage of the hydraulic fluid, which also rotate,

     there is produced in these sections of grooves such a variation of the wind speed of ot, we start,
 EMI16.2
 also from the sound of the flow, where the formation of incrustation in deposits and obstructions is excluded, solid particles,
 EMI16.3
 which will manage to settle temporarily, being antraindos with certainty by rinsing.

   The hydraulic crapaudino, which is the object of the invention, produces such a great self-relieving force that the sections of the choke grooves, in order to keep the double ports at leaks at a reduced value and consequently. variations in prossion which are
 EMI16.4
 reduce when the macliino rotates slowly, can have very small dimensions or cross section so what else, even in cases where we cannot absolutely avoid that the hydraulic fluid contains certain

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 EMI17.1
 : 1mpu.rot6, by Oxot1plo when the maohine tCl1'1ot: Lonno dana doo cogitions pnrt: Loul: Lbrouont 41tf:

  Rough laUol ot for ooutrrain mining works, always obstructing it well the section of the choke grooves or of an out of service adtso -total or partial of the orapaudino, hydrauliquo ost excludes harticaliéronon% effective are, in this case, the accelerations and decelerations of the current of the hydraulic fluid in the crapaudino which are produced in the machine with axial or radial pistons forming the object of the present invention and which alternate, at short periods of time, in numerous places distributed over the length of the around the frame, as well as the rotation of the lubrication fields and the discharge
 EMI17.2
 which is done simultaneously ot one synchronism avoo the rotation of the support back pistons,

   do rto that the offot of aeo-nottoyffl of the hydraulic toad, which is the subject of the invention, is much better than that of the known devices.



   As the quantities of hydraulic fluid which are
 EMI17.3
 each time to accelerate or, to delay are very potitos, the expenditure of enorsio nÓoooco.1ro to obtain neck nco61drntiona and these alternate deoelerationn is weak oxtramomofit, so that it practically does not influence the rondomont of the. hydrostatic machine.
 EMI17.4
 to oauso do the connection intormittonto ot do oourto duration of back pockets nooumulatr1oos distributed on all of the peripheral length of the ice distributrico by the n90ne back choke grooves 2rdvuoB on the sealing fado of the support back pistons, these sections prove;

  . while producing lao acno choke offot, have a larger cross section that sticks to the gicmont rainuro which has the shape of a closed ring ot which makes

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 EMI18.1
 part of the known conotracton modes. By the a6rmàiBéomon% do la. section trw1Dvoraalo dos tronoona do grooves didtran- glomont, we facilitate, on the one hand, the manufacture ot, on the other hand, we further reduce the danger of an obstruction or of a clogging of dry sections by back solid particles,
 EMI18.2
 whereas by aillouro and thin that the section do cos troncons is enlarged compared to glue of known dispesitons, it does not produce any increase in portos
 EMI18.3
 of oil duos to don euitçaq Another advantage of the axial piston madiino or.

   radial, which is the object of the present invention, resides in the fact that the intake holes which communicate with the cylinders of the piston back support, do not need to produce a throttling effect and can therefore have a relatively cross section. rumbles without Ion portos by
 EMI18.4
 leaks being ai11> aon% dào, It results that Io danger of the forma '<) a obatructionn and inorustations in these holes out also trba small i18mo aï in the hydrostatic machine making loL)

  Jot of the invention the number of accelerating impulses ot increase in hydraulic fluid
 EMI18.5
 naked in the hydrostatic orapaudino Qo4u proportional to the clonontanoc speed of the machine, we nevertheless produce, 4 using doo tvonço = do dtétrnnaloment grooves that connect only with a = Ibro intormittonto the $ acoumulatrioea pouch Do located on Ion 4eu :::

   mo1t: L4s to the ice cream dispenser, a quantity of equilibraco tollomont large of the quantity of hydraulic liquid consumed by the orapaudino which leaves, we have, at low speed, a quantity of liquid sufficient to obtain a good lubrication and pressure relief, on the other hand, for large
 EMI18.6
 vitoaccop the amount of co liquid is reduced by etranala-

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 EMI19.1
 Also to a dogr6 such that severe losses by leaks are avoided.

   In spite of the intermittent connection for the passage of the fluid, ontro the pockets of the soft halves of the ice
 EMI19.2
 followed by a fluid-tight separation of the oollovs.oi, the machine which is the subject of the invention runs very smoothly and without noise. In addition, by placing the machine on maroho or operating at very low speed, there is a quantity of hydraulic fluid large enough to avoid with certainty any metal-to-metal contact of the parts of the surfaces which slide over each other. the ice ot suppcrt back pistons, or even a seizure of
 EMI19.3
 these surfaces.

   It has been found that the hydraulic crapaudino is suitable according to the invention for very high pressures of hydraulic fluid, for example 200 to 250 atm or more, as well as for large variations in load and. for reversals of the direction of operation of pumps and motors
 EMI19.4
 hydrostatic system comprising such a crnpnud, ine, porno% to obtain uniform and absolute lubrication and discharge effective over the entire peripheral length of the crack.
 EMI19.5
 pritd, nv.

   with surprisingly weak port backs due to leaks and with reduced noise produced by the machine Dans los Ma oh les tlsonçons de c5trt. \ n8lO- grooves, mentally spared in the sealing face of the piston support and the aooumulatricos pockets foreseen in the active face of the distributor ice are established, in substance # on 10 mm a primitive circle concentric with the axis of rotation of the machine ot wntortadmont to another arrangement tying the object of the Ilinvontionp the segments) of groove of adjustment have a length, measured in the peripheral direction of said
 EMI19.6
 supporta having a value one louse greater than the eoartoment

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 EMI20.1
 and one })

  or more potito than the distance from back to back 'pockets which are found on the pressure side or on the suction or return side of the ice. In this way it is certain that each liver approximately half of the above-mentioned sections cover simultaneously and to a reduced degree, by their ends, the pockets which are distributed on one side, in the plane of the dead spots of the ice so that the hydraulic fluid, contained in the crapaudino,

   can be accelerated in many peripheral places to then be delayed everywhere simultaneously after a slight additional rotation between the support of the pistons and the ice.



   For an advantageous embodiment of the invention,
 EMI20.2
 the distance between the potici3 ac!., mulatriaos, in the region of the plane of the dead points of the dispensing ice is notable.
 EMI20.3
 However, more than the length of the choke grooves which all have the same length as the length of the back sections, in this way we obtain:

  i ^ nt that, for any angular position of the piston back support, a short circuit
 EMI20.4
 between the pressure side and Io the suction side of the water this excluded with certainty. z, this effect # it conviont all partieu- lieremont that their pockets which are found a. pro, m, td of the plane of the dead points have an eoartomont at least soft times greater than that of the pockets which are found in the other places of the rim of the ice.

   It is particularly advantageous
 EMI20.5
 that the distance against back pockets, which everywhere have equal become near the plane of the dead spots $ about twice as great which = * other places around the ice.



   Tour an advantageous embodiment of the invention is rolio softly soft sections of grooves

 <Desc / Clms Page number 21>

 
 EMI21.1
 throttle which are âiamétxalomont oppoodoi3prosPOctivcmcntt directly and continuously by soft inlet hole in the soft cylinders of the. piston back support for fluid passage
 EMI21.2
 The front hydraulics have the inlet holes, which are preferably substantially parallel to the axis of rotation of the piston support, have a diameter of about 1.5 mm at the narrowest edge.



   The ratio ontro the number of intake holes and their diameter is particularly advantageous because, for cos
 EMI21.3
 valcuree one obtiont, uno 18 rt, a flow abool = have sufficient liquid do graiBoC \ Go ot do discharge, then quo, on the other hand, los eootions t rruu3vo% "saloD free of cases holes, at the place where they are the narrowest They are so large that the danger of obstruction of the holes is not too large while
 EMI21.4
 that lastly the viscosity, which depends tortornon on the temperature monentvméo of the hydraulic fluid, exerts only a reduced effect on the dosage of the flow of said fluid.

   If the number of intake holes were greater, the smaller sections would in most cases have to be adopted as a consequence of these holes, which would make manufacturing
 EMI21.5
 more difficult, aulpiciitorait the dangers of obstruction and would make the permissible quantities of hydraulic fluid dependent on a high degree of temperature and of the viscosity of the fluid,.



   In a particularly advantageous manner, the free section of the choke groove sections corresponds to about one tenth to thirtieth, preferably to. about one-twentieth of the narrowest section of the intake holes. Do this in the same way the sections of the grooves

 <Desc / Clms Page number 22>

 The constriction generally has a free section of about 0.06 to 0.15 mm2, preferably about 0.09 mm2.



   An advantageous embodiment is obtained when the sections of the throttle grooves have nearly a transvorsal soction having the shape of a rectangular triangle with a maximum width of about 0.6 mm and a maximum depth of about 0 , 3 mm. Such a groove can be formed simply with the aid of a milling cutter and provides, in addition, for the usual dimensions of hydrostatic machines doo particularly favorable conditions for the lubrication and the discharge near the hydraulic slider.



   The sections of the throttle grooves are preferably curvilinear in the longitudinal direction, but it is also possible in certain cases to give these sections a reotilinear shape. Preferably, the number of accumulator pockets formed in the dispensing ice is between approximately 14 and 18.

   On the other hand, the number of choke groove sections corresponds to approximately 16 to 20 and is therefore two more than that of the back pockets * In this case, the length of the choke groove sections, which all have the same length, is such that it is included within about between the twentieth and the twenty-fifth of the peripheral length of their original circle.



   In order to obtain a rapid and efficient acceleration of the quantity of hydraulic fluid contained in the carpau- dine and a uniform formation of the lubrication and discharge fields, the sections of throttle grooves are advantageously arranged and dimensioned in such a way that all the sections which are on the pressure side and all

 <Desc / Clms Page number 23>

 sections which are on the suction or return side of the dispensing ice cover, by their two end parts, when the overlap is as large as possible, two neighboring pockets over a length which is greater than their width.

   In this way it is certain that between the ends of the sections and the pockets there is a nil or insignificant throttling effect, the throttling of the hydraulic fluid in the slider being determined, in subsxtance, by the free section and the useful length of the sections.



   In addition, the sections of the throttle grooves can be offset, in the direction mediale of the sealing face of the support of the pistons :, in such a way that, balancing the rotation of the support oe, the aforementioned sections pass alternately over the formed pockets. in the distributor glaco to the external and internal parts of their circumference with respect to the axis of rotation of the machine * In this way, the active faces of the slider are also fed in their outer and inner marginal areas with the lubricating liquid and do deohargo these faces being therefore lubricated and discharged uniformly ot offioa- tion over their entire width.

   In addition, the sections can also be given a greater length, which makes it possible to obtain, with the name transverse coction, a greater strangulation effect which manifests itself above all when the sections are not rounded in the direction of the perimeter or tangential- lemont, but form an angle of about 160 @ to 13 @. in the same sound, with respect to the corrospondant radius of the sealing face of the support of the pistons, being arranged on tangled teeth with respect to each other.

   Solon another weight, the sections form alternately an angle of onvi-

 <Desc / Clms Page number 24>

 
 EMI24.1
 ron 6t to 1308 donations doa opposite direction with respect to the radius>; corresponding to the sealing face of the. back support pistons being arranged in the form of a roof relative to each other. very.
 EMI24.2
 



  Los accompanying drawings show, as an oxonpioaj. several embodiments of the invention.



   Los fig. l ot 2 show, respectively one longitudinal ooupo and one transverse section according to II-II fig. 1, an axial piston pump established in accordance with the invention.



   The figure shows an elevation along the arrows III-III fig. 1, the sealing face of the piston support of the aforementioned pompo.



   Fig. 4 shows, one elevation as on fig 2:
 EMI24.3
 how the accumulatriocs pockets are connected ontro them by the distributing grooves for the passage of the liquid under pressure.
 EMI24.4
 



  Figure 5 shows, aemblablemont to eïg * 48 the distributor grooves in a different position.



  The end. 6..montro $ h larger scale and we cut as on fig 1.! a part of the support of the pistons ot the distributor ice, these parts being placed at a distance from each other.
 EMI24.5
 



  Los fîg, 7 ot 8 show, schematically ot somblarbionont in the freeze 4j the distributing grooves established according to a variant, the aupport dos pistons occupying dos different positions.



  Los freezes 9 ot 10 showpsemblablomonttdos distributor grooves established according to another variant.



   For loo modoo do embodiment shown on the dos- sine, the invention is applied to an axial piston pump

 <Desc / Clms Page number 25>

 
 EMI25.1
 real and reversible, corn is not obvious that it does not apply just as well to its radial piston pompom ot to all loo pompoo ot praised the hydrostatic aetoura $ of the moment which they are supplied by a distributricet ice cream More ep601nlomont, the invention is applicable in all cases for which the light of rofoulemont is made up of ma, n3, xo such that it subdivides the total flow of the pump on at least two rofoulde partols separated from each other, whose fundamental properties '(discharge pressure $ flow rate and discharge speed)

   
 EMI25.2
 are the unos back others independent? these partolo currents which can be pre-emitted independently of each other. We sign by 1 a support of pistons, one cylindrical substance in where its + provided an odd number of cylinders 2 which are distributed in the peripheral direction
 EMI25.3
 said support him on a mono ooràlo primitive do this one with dos uniform spacings, these oyl1ndroD being para2.lbloo between them and to the longitudinal axis of the piston back support.

   In the cylinders 2 can slide axially along with a manibro
 EMI25.4
 étanoho back pistonc 3 of which los tigos 4 are connected by back ball joints to a tilting or adjustable tilt plate 5.
 EMI25.5
 For the embodiment shown on the figure 10 support 1 of the pistons and 10 tilting plate 5 as well as the piston rods 4 which roliont them are housed in a common housing 6, a cylindrical substance, including a front wall
 EMI25.6
 is crossed by the oxtrétaité of a shaft 7 connected to a drive motor ot ronduo dtanoso relative to the housing 6.

   The ontralrnonx shaft have journalled in an interior access 8 of CltU'tOt 'hl' 1 \ 1110 of a roulomont à rou1ot! .Wt; cylindrical 9 while the opposite end of the shaft is housed in a

 <Desc / Clms Page number 26>

 
 EMI26.1
 ball bearing 10. The middle part of the shaft? is made integral in rotat1on, by a key 110 or. for example crabota, a corner or. 7.4, u from.

   support 1 of the pistons so that the shaft .7 drives. said support weighing that the pistons 3, coupled to the tilting plate 5 by the piston rods 4, listen to a back-and-forth movement The piston back support 1 is guided by his face
 EMI26.2
 front 12 formed Doua the form of a face dtêtOO10hé1tê, in a sealed manner by a distributor glass 13 which cannot rotate in the casing 6 but can move this # to a limited degree in the axial direction of the drive shaft 7 . The ice cream bag behaved, as clearly visible on
 EMI26.3
 los fig. 2p 4 and 5, d3.stributrà.coay lumibro, namely a suction light 14 and a do rofoulomont light 15.

   The cylinders 1 of the support are connected by back passages 2a
 EMI26.4
 to the dtdtancliéît6 face of the support 1 and communicate suooosoi- vonant .. when the support rotates with the ports 14 and 15 to allow 10 pascaco of hydraulic fluid. The slaco distributrioo is tight, by at least soft diametrically opposed proraouxce pistons (not watches), respectively connected to the suction duct 6a and to the delivery duct 6b
 EMI26.5
 against the face dld4uanohdîtê 12 of the support 1 of the pistons.

   The active face of the dispensing valve 13t which slides on the face of etanoheity 12 of the read support is subdivided, as can be seen on the fis. 2e 4 ot 5, we have a distribution part 13a which includes the lights 14 and 15 ot
 EMI26.6
 a bearing face do ora.paudino 13b, by a groove or separating groove 16 which has a shallow depth and which communicates without pressure, by holes 17 and 18, m with the interior of the housing, Externally the bearing face 13b

 <Desc / Clms Page number 27>

   this delimited by a flange 19.
 EMI27.1
 



  The bearing face of the crapaudino oot as visible on Ion fias 2e 4 and 5p provided, a, until close to the plane of the dead points' "has a multiplicity of pockets l1ooUQulntrioOB oiroulairos 20 established at a low level of the unoa others and plaodos on 10 primitive cord marl, coa pockets having the same diamonds and a term vv6e There is a number of bear pockets oorroopond to sixteen for the examples mounted on the eight on the repression side and eight on the oapira- tion side or of return of the ice cream dispenser The distance from against to center back pockets, do elaruc cbtd of the TT plan don dead points, decreased by 1 on the fiS- 2 ot their aour.

   In this rdsion of pourthte, oat desisai4 by 9 z proximity to the Tx plane llêcartomont z soft back pockets volz zincs is larger quo 10 double do .ieovtomont aforesaid The diotanoo do against against soft back pockets close to the TT plane is in pou almost soft times greater than the distance back pockets which are on either side of this plant The arrangement is therefore practically as if, for back pockets 20 all having the same spacing, ot the single distance do against against , the pockets which are in lo plan TT had been deleted.



   For the embodiment shown on Ion fig. 1 to 6 are provided soft open intake holes 21, distributed
 EMI27.2
 except for uniforncaont on the perimeter of the support 1 back pistons, these holes therefore being, in substance, diametrically opposed and emerging directly, by one end in a cylinder 2 of the support 1 for the passage of the hydraulic fluid, whereas 'it opens, by its other end in the zone of the width of the annular face, limited by the pouches 20,

 <Desc / Clms Page number 28>

 
 EMI28.1
 ice 13, 00 = 0 visible on the tigo 3 coe holes at 1 '' Ô are, for this example,

     inclined at an acute angle on the axis of rotation of the support 1 back pistons but it is preferred to orient them parallel to this axis.



   Comma visible more specifically in figs. 3 to 5
 EMI28.2
 and 7 to .0 we spare in faoo 1 étanah.t 12 of ouppoet W'1 oo: r.ltain number of trongona 22 of grooves dl tStrMSlomctlt co number being oupÓrioU, 1 'of dowe to glue pockets 20 (jos sections have a length reduced and equal for all are spaced from each other at close to the same distance
 EMI28.3
 .

   For the zonard example on lod fia. 1 to 6, the sections 22 have a curvilinear and circular shape conformed to the peripheral direction and they have a length! 1 which is between about one-twentieth and one-twenty-fifth of the total length of their primitive circles. width,
 EMI28.4
 in the plane of the sealing face 12 of the support 1 of the pistonayost of approximately 6 mm, whereas for a cross section trian7.a.ro their greatest depth is approximately 0.3 mm,
For the embodiment do dos freezes 1 to 6, the sections 22 being on the same pitch circle that the outlets back through the intake hole 21 which are close to
 EMI28.5
 in the middle of the length of soft sections 22a,

   22b diametrically opposed for the passage of the hydraulic fluid,% At the
 EMI28.6
 place soft back holes z one could, if necessary, use a larger number of ooa holes but in most cases one prefers so lîmitor 4 soft holes of which 10 inside diameter, at the narrowest place, corresponds to 1.5 mm 60 diameter for the hole of the example in fig, 1 to 6, is about twenty times larger than the free section of the sections 22.

 <Desc / Clms Page number 29>

 



   The length of the sections is a bit. greater than the distance z which separated, on either side of the T-T plane, two neighboring pockets 20 but a po smaller than the distance t between the opposite do cos pockets on each side of the T-T plane. The distance k between soft successive sections 22 corresponds, for the example shown in fig. 1 to 6, up to 70-80% of the largest diameter b of the pockets 20 and is a high multiple of the width A of said sections 22.



   For the example according to the figs 7 and 8, the sections 22 are inclined with respect to each other, making an angle a of about 60% at 130 @ with the corresponding radius r of the support back pistons to the part median of said sections.



  For this example, the sections 22 are rotated, but nothing prevents them from bending slightly in the longitudinal direction. Also in this case and as shown in figs 7 and 8, the pouch 20 established on each side of the TT plane. are interconnected, intermittently, by the sections 22 for the passage of the hydraulic fluid while after an additional relative rotation of the support 1 of the pistons with respect to the distributor ice 13, the poohos 20 are separated los unos des others in a hydraulic fluid-tight way.

   On the other hand, a short-circuit between the halves of the ice, which are located on either side of the T-T plane, is also excluded for co-implementation. In this case the two intake holes 21 are also established at diametrically opposed points of the mirror, approximately in the middle of the soft sections of which only the section 22a is visible in Figs, 7 ot 8.



   For the embodiment of the fig 9 ot 10, the sections 22 are offset in such a way, in the direction

 <Desc / Clms Page number 30>

 
 EMI30.1
 radialo of the sealing face 12 of the support 1 back piston, its that these sections, when the support 1 rotates, pass a1% or-, natively on los aocumulatricos 20e formed in the bearing face 13b of the distributor glass 3 to the parts which DO find 1; adio.loJ: 1 are on the outside and outside of their perimeter.

   In this case, the sections 22 can be rectilinear or curvilinear and can be drawn almost tangent to the primitive corcloses which pass through their medium for the example in fig. 9 and 10 the sections 22 offset from each other are slightly curved
 EMI30.2
 we agree with the curvature of their primitive circle.

   The distance between the sections 22 ost, in oc case, also fabric qi,% ot oo = o visible in fig. 2 and for a determined gangular position of the support 1 of the pistons, all the pockets which are on the discharge side and all the pockets which are: on the suction side or on the return side of the
 EMI30.3
 glaoof4tributricO 13, one being uniform ± mounted on -'Ir "collo-oï, are connected to the intake holes 21 while after a certain relative rotation ontro said support 1 ot said mirror 15 (fia * bzz the link for the paseagc hydraulic fluid is interrupted again for the pockets 20 ot the inlet holes 21,

   
 EMI30.4
 The function of the embodiments shown in the drawings is as follows.
 EMI30.5
 When actuating the support 1 of the piston, via the drive shaft 7, using the motor not shown, the pistons 23 so move in a reciprocating motion, suck, in the position shown and through the port 14, hydraulic liquid out of the suction pipe 6a and discharge this liquid through the port 15 and

 <Desc / Clms Page number 31>

 the conduit 6b leading to the user station.

   The remaining pistons (not shown) are also stressed and resected by the pressures prevailing in the suction duct 6a and in the delivery duct 6b to clamp the distributor ice 13 against the sealing face 12 of the piston support 1. ..



   By the inlet holes 21, connected to the cylinders 2, the three sections of the distributing grooves 22a, 22b and 22o are supplied with hydraulic fluid under pressure, so that around the outlet of each hole 21 and around each section 22a, 22b, 22c, forms a field of lubrication or do discharge in the existing seal re the sealing face 12 of the support 1 and the bearing face 13b of the glass 13.



   As the sections 22 are longer than the distanced ± ontro soft pockets 20 which follow one another in the peripheral direction of the distributor ice, on either side of the TT plane doc dead spots, all the poohos 20, as visible more especially on figs, 4, 7 ot 9, both collos which are found on the delivery side as well as ocllos which are on the suction side or on the return side of the glass 13, are roliées ontro them in an immediate way to the passage of the pressurized liquid, so that the liquid lubricate or discharge, discharged through holes 21, is accelerated laying pou do tomps, ot simultaneously,

   several points around the perimeter of the hydraulic crapaudine, ot may flow for a short period to the periphery of the glue. It thus forms, starting from the intake holes 21 ot in the seal formed between the sealing face 12 said support 1 back pistons and the active face 13b of the distributor glass 13, a pressure of the hydraulic fluid which goes we decrease towards the TT plane.

   Los champs do

 <Desc / Clms Page number 32>

   lubrication and discharge thus formed not being able to propagate beyond this plane because, on account of the notably greater distance of the pockets which are in this periphenic region of the hydraulic valve, any short-circuit between the delivery side and the suction or return side of the ice distributor ost exelu,. After a low amplitude rola- tivo rotation between the support 1 back pistons endowed with the distributor glass 31 the connection for the passage of the hydraulic fluid between the pockets 20 is again interrupted, as seen in fig.

   5, 8 and 10, so that the flow of this fluid in the hydraulic crapaudino decelerates to zero speed At the same time the pressure of the hydraulic fluid, with the ocoptn of glue which prevails in each back sections 22a ot 22b which ost continuously connected by an inlet hole 21 to a cylinder 2 of the support 1 of the pistons doscond to louse near to zero value.

   This process is repeated, during a complete revolution of the support 1, as many times as there are do sections 22, so that a pulsating but strongly slowed flow of the hydraulic fluid is obtained, at intortal intervals. very short times in the peripheral circulation of the hydraulic slider. By modifying the number the constitution and the dimensions of the back pockets accumulators 20 and the sections of the choke grooves
22, it is possible to adapt the lubrication and the unloading of the aotivos faces, which follow one another, of the distributrico glass 13 and of the support 1 back pistons to the conditions existing in each case.



   For the device shown in fig. 7 to 10 are obtained, by the offset of the sections placed obliquely with respect to each other or by heavy offset in the

 <Desc / Clms Page number 33>

 
 EMI33.1
 radial direction and its tangontiol location, a slightly uniform distribution of the lubricating liquid and of discharge over the whole width of the bearing face of the urapaudino. The sections 22 open into 100 pockets 20 when they oooupont the position in the loo they connect between- '
 EMI33.2
 ollos los pockets 20 for the passage of the hydraulic fluid, except for tarwontiollomont to the sides apart 11 \ 1J \ d Q the other of soft neighboring pockets.



  00ntraitcncnt to co which was shown on the dosa3.nst it is possible in certain cases to make the inlet hole 21 open, a reduced distance on the side of the sections which oc find in coz peripheral places of the faoo of sealing of the support 1 back pistons, do sorto quo los sections 22a ot 22b, neighbors do these holes 21, are not connected directly but bion indirectly to these holes. In this
 EMI33.3
 case, the arrangement can Ctro such that the direct connection to the outlets back holes 21 ot the sections 22a and 22b back detangled grooves will take place, uno intermittently) by the pockets 20 mixed in the active face 13b do the glaco 13 on the same primitive circle.

   It is also possible to give the sections 22 a wavy or zig-zag shape.



  Do more, we could shift the pockets 20 provided in the active face 13b of the mirror 13, so that their whole
 EMI33.4
 have a shape one zig-zagt In this case we must also constitute the sections 22 in a tollo way that they can rolior,
 EMI33.5
 by intormittenoe, all the pockets 20 do the face 13b unos to the others for the passage of hydraulic fluid.



   While generally the sections 22 are threatened in the sealing face of the support 1 back pistons ot the pockets 20 in the active face 13b of the glaoo 13, we could

 <Desc / Clms Page number 34>

 
 EMI34.1
 also adopt On principle the reverse arrangement, the po9hos. '(20 being provided àoew the face of tnoh.t of the support 1 and
 EMI34.2
 
 EMI34.3
 the sections 2a in the active face 13b of the ice, In t .. this case lofa pochqu 20 dovraiont 8tre distributed over the entire perimeter of the dldtanchditè face of the support 1, their ooartomont and the distance of against 4 against being everywhere equal.

   However, the aubsiator should then be left between the sections 22p 4 near the plane 1-1 back the dead points of the ice an intorvallo such as on the delivery side and the suction side 1>) around the Claco the pockets 20 prdvuos on the support 1 $ may btro bound from uno material mtorni% tont9 by los.? i; sections and btra onouïto adparéoa in a 4tanoho manner to '/: j. hydraulic fluid while a connection for the passage of this fluid 4 tracera Io plan is ronduo impossible, Dans .ui.do txaroxa .c pltxn T.T oot randuo impoeo.b.o. In 00 oao and do pr6aoroot each soft back pockets 20 diotx lomont opposite should be rolidc diroctonont ot continuol- .anant-4, a cylinder of the hydraulic machine for the passage of the hydraulic fluid.

   The distance between the pockets 20 ost equalomont, in 00 cases., Less than the length of the back sections 22 at a do-rd such as the rotation of the support 1 back pïstona # all the pockets which are on the suction side. "j or from the return of the slack are each time connected n.ltoxnati ..:, vomit by the sections 22 between ollos ot to the admission trott 21 which finds from the m8no side of the TT plan for the pasoago of the hydraulic fluid, these pockets to, nt onsuito Bdparéos 4 new ..



  '- in a way of detancho said fluid, In general it is good ,,' 'to adopt then an arrangement for which the poohos are distributed uniformly on toto the length of the perimeter
 EMI34.4
 do the sealing face 12 of the support 1 back pistons, while the distance between soft sections 22 at the locations of the pin
 EMI34.5
 T T of the ice 13 is notably larger than the diametrofi

 <Desc / Clms Page number 35>

 a pocket 20. It is then particularly advantageous that the distance between the sections 22 at the locations of the plane
T-T of oorrosponde ice 13, approximately $ k the length of a segment 22.



   Except for these differences, the construction and arrangement of the sections 22 and the pockets 20 are the same as those described with reference to the examples shown in the drawings.

 

Claims (1)

EMI36.1 R E V E N D I C A T I O N S. 1) The invention relates to a hydrostatic machine with axial or radial pistons according to the main patent n PV 18.509 filed on September 30, 1965, this machine comprising a distributor ice prevented from rotating and on the active surface of which, which comprises the distributor openings, slides the sealing face of a piston support in a hydraulic fluid-tight manner and on which are distributed approximately annularly around its axis of rotation, a large number of distributor grooves of short length which extend substantially in the peripheral direction of said support, at least one of these grooves being connected, by an inlet hole having a reduced section, preferably directly and continuously, to a cylinder of the support of the pistons for the passage of the pressurized fluid while on the active face of the distributor glass are distributed annularly, roughly on the same pitch circle as the distributor grooves a large number of accumulatrics pockets whose sneer in the peripheral direction and on each side of the plane of the dead center of the distributor ice, is less than the length of the distributor grooves, so that, during the rotation of the support of the pistons, at least some of the pockets which are located on each side of said plane, are intermittently connected to each other and to the supply hole which is located on the side of this half of the distributor glass for the passage of the hydraulic fluid, while a short circuit between the two halves of the plate distributor is excluded, characterized in that the distributor grooves are constituted by sections of throttle grooves whose free cross section is significantly smaller than the smallest cross section of the inlet holes, The machine as specified above may, in putre, have the following characteristics considered separately or in combination: 2) the choke groove sections have a length, me- <Desc / Clms Page number 37> sure in the peripheral direction of said support, by a value a little greater than the spacing and a little less than the center-to-center distance of the pockets which are on the pressure side or on the suction side or return of the ice; 3) the spacing between the accumulator pockets, in the region of the plane of the dead points of the dispensing ice, is notably greater than the length of the sections of throttle grooves which all have the same length; 4) the pockets which are located near the plane of the dead spots have a spacing at least twice as large as that of the pockets which are located at the other places of the periphery of the ice; 5) the center-to-center distance of the pockets, which is everywhere the same, becomes in the vicinity of the plane of the dead spots about twice as great as at the other places around the ice; 6) only two sections of throttle grooves which are diametrically opposed, respectively and directly and continuously, are connected by two two-cylinder inlet holes of the piston support for the passage of hydraulic fluid; 7) the intake holes, which are preferably substantially parallel to the axis of rotation of the piston support, have a diameter of about 1.5 mm at the straightest point; 8) the free section of the sections of the throttle grooves corresponds to approximately one tenth to thirtieth, preferably approximately one twentieth, of the narrowest section of the inlet holes; 9) the sections of the throttle grooves have a free cross section of about 0.06 to 0.15 mm2, preferably about 0.09 mm2; 10) The choke groove sections have approximately a cross section in the shape of a right triangle with a maximum width of about 0.6 mm and a maximum depth of about 0.3 mm; 11) the choke groove sections have a curvilinear shape in the longitudinal direction; 12) the number of accumulator pockets formed in the dispensing ice is between envyon 14 and 18; <Desc / Clms Page number 38> 13) the number of throttle groove sections corresponds to approximately 16 to 20; 14) the. length of the throttle groove sections, which all have the same length, is such that it is approximately between one twentieth and twenty-fifth of the peripheral length of their pitch circle; 15) the sections of throttling grooves are arranged and dimensioned in such a way that all the sections which are on the pressure side and all the sections which are on the suction or return side of the distributor ice cover, by their two end parts, when the overlap is as large as possible, two) adjacent pockets over a length which is greater than their width; 16) the sections of the throttle grooves are offset, in the radial direction of the sealing face of the piston support, so that, during the rotation of this support, the aforementioned sections pass alternately over the pockets threatened in the dispensing ice to the external and internal parts of their periphery with respect to the axis of rotation of the machine; 17) the eyelets form an angle of about 60 * to 130. in the same direction, with respect to the corresponding radius of the sealing face of the support of the pistons, being arranged in sawtooth with respect to one another; 18) the sections alternately form an angle of approximately 60-130% in opposite directions, with respect to the corresponding radius of the sealing face of the support of the pistons, being arranged in the form of a roof with respect to each other; 19) the sections of throttle grooves are formed in the active face of the glass and the accumulating pochas are established in the sealing face of the support of the pistons, each of two of these pockets, preferably diametrically opposed, being connected, by an intake hole, having a cross section significantly greater than the free section of the sections, preferably directly and continuously to a cylinder of the piston support for the passage of hydraulic fluid; <Desc / Clms Page number 39> 20) for the arrangement according to 19, the pockets are distributed evenly over the entire length of the circumference of the sealing face of the piston support, while the distance between two throttle sections, at the locations of the plane of the points dead from the distributing ice, is notably larger than the diameter of a pocket; 21) for the arrangement according to 19 or 20, the distance between the sections, at the locations of the plane of the dead points of the distributor ice corresponds approximately to the length of one of said sections.