DE2001484A1 - Hyd? Atic eno? for pumps and motors - Google Patents

Description

öegenwärtig are ■ "ei hydraxiliselien Puiupen axial piston motors and often Betriefosdrücke in Jiereiqlx 550 'kp / cm erforderlicti can etitwiclcein the liohe Schrägdrueklcräfte on the bearings, which _are: -for rotation; äadertie -the ingredients: -If the pumps or such Mptoreti However, if they are somewhat erratic, the angle of the pressure forces can change considerably

Units of the above type known in the art have hydrostatic buttons on the socket end of the Piston or connecting rods and a passage through each Rod, and the associated piston used, making the assigned button with the cylinder pressure of its rod

009831/1074

Dipl-Ing, Martin Utht, Dipl.-WirfiCte-lnti.Axel hlcinsmonn, Dlpi.-Phys. Sebasfiait Herrmqnn

β MlJMCHEN %, TH ERES I ENSTRASS E 33 · rels'on 2312Ö2 - Teleg-ainm-Adressa iipai. 'Miiuchen. -

Doyer.'y «feii>;. baak Munich, Zwäigil. Otkctf-von-Miller-Ring, Kiä.-Nr. 802495 · Poslschack-K • '• .to: Mw-äicj ^ iNr. J633 97 BAD ORlGINIAI

Examples of such known arrangements are illustrated in US Pat. No. 2,241,7oi and US Pat. No. 5 1:21 Hlb. One of the difficulties with the known arrangements is that the pressures in the i., Age ■■ -drucks can change very violently, luunehuial exceeding the maximum pressure in the unit and sometimes falling below the minimum pressures required for precise storage are required, especially during the intake stroke of the associated piston. This fact and the stabilization problems for the individual buttons that occur at high speeds have left room for significant improvements.

Furthermore, the production of hyUroatatischen Button are stored and the place ι »lerliche S troumuu.siaediuHt-zuf unclean situation for hydraulic ■ iia-egf'ta With Axiali.olben ^ 'jfiiiü the prior art expensive and koupliziert, Far is τ, The key replacement of the button bearing is often impractical, if not soyir impossible. Considerable difficulties arise with regard to the correction of soiling or , first of all, problems with the known arrangements, and if one of the knobs no longer works properly (as a result of clogging or soiling ;, the thrust bearing for this piston rod is completely lost »This circumstance can quickly lead to a pressing of the associated running surface on which the button bearings run, and consequently lead to failure of the entire thrust bearing position.

Furthermore, many of the buttons known in xeehnik can be used. lageranordnuugen work effectively with mechanical bearings cooperate in order to jointly reduce the pressure forces around the pressure plate or ring arrangement, which change with the displacement angle to absorb, since it is difficult to simultaneously determine the exact distances for the two bearing arrangements in such Maintain facilities,

BAD OHlGiNAL ÜO9831 / 1O74

Most of the above "" and difficulties can be overcome by the hydrostatic pressure bearing arrangement according to the present invention while achieving an "improved performance." The / uilngo gomiid of the present invention "is -aueli more economical than Uie systems according to the status of the Tc '<':! inilt. _t Basically tvit-d κίο in hydraulic Axialkolbeitaggre ^ ateu vo ^ turns, (Ii- upliror «I'leuelstangen, dl» in a g-ciiiciusatiieu, si ^ h are, η t <? encompasses m-eleven reru pockets, which are arranged in the unit and the imiaug of the pressure plate arrangement, nowie each pocket with a source for pressurized flow medium verbiwle.nrteu Uurehgang, as well as several buttons bearings, which are accommodated in every Tascite, with each iitiopflager comprising a pressure which is effective in conjunction with a surface on the pressure slat arrangement. "assigned iasche stands, as well as a circular threshold that surrounds the recess, so that the 'pressure acting on each thrust bearing the pressure tuck' in the direction of" presses the surface, so, üass die - "Now -e a-af ei now hydroetatiBchen film worn "is _c Λ ^Γ οrzne, sweise" rc «rde-; i die . knojiflager in half-croiss "feirreigeu" ■ groups "under Drunk Eeset, whereby the one group durcl. üurchgafige is pressurized , which the Ku op f lager mi. t connect the ulnar part of the unit.! WUhreud the other group is put under pressure by Xhirc-h-giiuge, the aie. Button stock iiuit the AuslaOseite 'of the unit connect "This is a better pressure balance iilr the calibration iu Uusfan.gs-richtutig ■ äodei-rideTi compressive forces and" the Druckplxitteiianoxummg is geschaffen- ,, Furthermore, you will raw tiiekiläche special training of pressure. . the possibility of the individual buttons tilting slightly as a result of the hydrodynamic structure of the film, because the greatest leeway at the fore chewing of the head exists, which is caused by the rotation of the one with the thine

BATH ORIGINAL 009831/10 7 ^

200H94

Button cooperating surface is caused on the pressure plate assembly. The arrangement briefly described above enables quick and easy button exchange, which was not possible with training according to the state of the art.

The invention will become more apparent with reference to the accompanying drawings, in which

Fig. 1 a «! Sejinitt is viewing a pivot assembly for uiu hydraulic axial piston unit is, in dej lijc new type of hydrostatic push of a button— lagerunji'ge is illustrated,

Fig. 2 is a, in the frj »view of the pivot arrangement, W (VK:! Lixa iiiiopflager from the assigned to them yes; ι .nu in which the journals are removed and in ;;« s t. Ri <? H <· I th Lines the pressure medium connection canoe illustrates sitid, which connect the individual rasv'teu with each other,

Fig. 5 eitHi sociio.inatic illustration of the sohrags Pressure forces are applied to the hydrostatic Iviioj »flauer and an associated raechnnisob.es Act camp,

Fig. 4 shows a part of the pivot pin aufaüilduug, in which one of the button stores in Section is shown,

Fig. 5 is an illustration of the theoretical pressure.

profile transversely to the pressure piece of the button bearing

is and
6 to 9 plan views or sectional views of

two differently designed button storage areas

or -prints are.

The hydraulic axial piston unit by which the present invention is illustrated is detailed

/ BATH 0 0 9831/1074

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in the USA ~ P _a tentschri ^o ft 3381472 described. Bozug is referred to in this patent specification for the details of construction and puncture of such an assembly. In Fig. 1 only the trunnion arrangement of the unit together with some associated parts is illustrated, since these individual parts have mainly to do with the pressure problems which arise hydraulic units are used in an advantageous manner. It should also be pointed out that these hydraulic units can act both as hydraulic pumps and as motors. Ground "- additionally the pin 10 forms the support structure for the pressure plate assembly Ii, which is rotatably mounted in the center of the pin on an inner roller bearing 12 and an outer Boll bearing ± 3", the latter is held by a bearing block Ik, the threaded bolt 15 is screwed to the pin. . As shown in Figure 1, tapered roller bearings can be used and arranged to DFIE pressure plate assembly to fasten ¹¹ "comprises the hollow pressure AufnahmekeiJLe arrangement 16 for receiving a drive shaft and a gimbal * | joint for the drive of the cylinder drum (not shown) "Furthermore, a circular ring 17, which rests on the roller bearing 13 and is connected to the pressure plate arrangement, limits the axial movement between the two roller bearings", ¹

The inner part of the pressure plate assembly 11 comprises a radial flange 18, on the circumference of which the roller bearing 12 carries the assembly "In several cavities 19, which are arranged in circumferential direction around the inner surface of the radial flange, find the spherical ends 20 of pistons «Or connecting rods 21 and are ^{held in these cavities by:} spring washers ^ 22, Bie connecting rods«

009831/1074

2OOU84

Rods are connected to pistons (not shown) in the cylinder barrel 23, the apertured surface 2h of which sits on a valve plate (not shown). When the apertured surface of the cylinder barrel is at an angle to the radial flange 18, they move the connecting rods back and forth in the drum, their associated pistons being acted upon by hydraulic pressures. This causes forces to be exerted on the pressure plate assembly by the connecting rods, and a passage 25 through each rod can supply lubricant into the cavity 19 from the pressure side of the associated piston in a known manner.

The angular position of the connecting rods 21 with respect to the pressure plate assembly 11 during a positive displacement in the hydraulic unit is illustrated in Figure 3, in which the vectors A ^1, ii * and C show the pressure forces generated by the pressures A, α and C are caused that act via the associated connecting rods. As it can be seen from Fig. 3 ', the pressure forces change in the circumferential direction around the pressure plate arrangement, and can each be shifted into an axial component 30 and a radial component 31. There are, the variable axial components of these pressure forces on the the present invention relates to providing better pressure equalization than was previously possible in the prior art arrangements. The shape and arrangement according to the present invention has the following effects! and advantages: The hydrostatic buttons take a part | are negated caused the 'anti-friction bearings of the piston pressure load to thereby lower loads. This enables the use of smaller anti-friction. bearing and brings with it "in" J a longer service life of the bearings · j

009831/1074

■■ '"■" 200 HÖ4 - 7 - - ■:. ; ■ ■ ■ ·

The amount of vxm produced by the hydroscopic buttons The support or bearing is constant for a certain pressure, but the axial component is the piston pressure. force changes with the displacement angle * The anti-friction bearing absorbs the difference in axial loads as well as the radial component of the piston pressure force.

For this purpose, the pressure ring 32 is by means of a pin attached to one surface of the radial flange 18 so that its pressure surface 3 & 'can form the barrel of a separate hydrostatic bearing - which is connected to each of the buttons will. i> he individual links 35 are around the circumference arranged around in pockets 36 and 37 in "the pin IO, like it is most clearly veransciiaxilicht in Fig. 2 * the tabs

36 stand over passages 30 and 3-9. in fluid flow binding with one side of the aggregate, - while the! pockets

37 in fluid communication through passages 40 and 41 stand with the other side, thus forming the pockets. 36 a semicircular "group", while the pockets 37 are a another semicircular "group" form, whereby the one Group of buttons, always under the inlet pressure of the unit while the other group is under the outlet pressure of the unit stands ",

The use of two semicircular "groups ¹¹ , which are guardians of the inlet * - or *" outlet pressure, prevents the occurrence of individual pressure peaks on the individual pistons and enables the pressure loads to be distributed more evenly to some of the individual button bearings due to the rigidity of the pressure plate arrangement. The use of the buttons in high pressure and low pressure groups allows the force center of the liydrostatic button forces to be close to the force center of the

ν BAD 009831/1074

200U84

Axialko] pressure forces to be arranged, whereby the moment imbalance on the> pressure plate is kept as low as possible. When the buttons are provided in groups and arranged as indicated, the pressure in each group is constant and does not fluctuate between the outlet pressure and the outlet pressure as it would if the button with the piston and would rotate of the rod and would be lubricated through a passage dxirch each piston rod. The passages are arranged so that the higher pressure is on the "group ¹ * with the highest load, regardless of whether the high-pressure side ^ the inlet or outlet side of the unit is. With such an arrangement, further advantages can be achieved and the exchange of buttons can be considerably simplified.

The general shape of each button 35 is clearest shown in Figs. Ί and 9, from which it can be seen that each button eintm head portion 50 and a cylindrical base 51 includes, in which a i \ ut 52 is formed for a seal 53, which prevents the leakage of pressurized Flow medium around the button base from the pocket 36 (or 37) and the passage 38 or 40 prevented. It is it can be seen that the individual button in the pocket assigned to it has considerable freedom of movement.

The cylindrical base 51 of each button is preferably hollow and may have a filter or screen 5 ^ over its mouth or opening 55 which communicates with the pressurized flow medium in the associated pocket, as is most clearly shown in Figs 9 is shown. The cylindrical base sits looker in the pocket so that the button can be tilted about the center line of the pocket. This arrangement enables the individual button to run smoothly on the associated surface "^ k" and that the bearing formed by the button

009831/1074

200 H 84

less duroh the Verwindungskrafte is impaired, the ttenanordnuiig be in the Drückpia due to the high pressure 1 as obligations to tr et en _o Bi e Unbutton e, the a b it t IMMT en degree of Kippfaeweguugs ~ and having axial freedom of movement, can to be sure the need for "* parallelism between the pressure plate and the pivot, changes in the spacing between the pressure plate and the pivot, differences in the running distance required with changes in pressure, and / or temperature adjustment"

In principle, each button 35 forms a separate hydrostatic bearing, the pressure piece or the surface 56 of the button being provided with a recess 57 which is connected to the pressurized flow medium in the associated pocket via a flow restriction or constriction ; each button has a raised circular sill 58 ^{which mates with the flat surface 3 2} ^ of the thrust ring 32 which forms the runner portion of the bearing.

As the pressure ring rotates, a certain hydrodynamic bearing effect occurs together with the hydrostatic bearing, which is formed by the flow of pressurized flow medium over the threshold 58 of the pressure piece or the surface 56 and acts in the recess 57: The movement of the pressure ring in the direction of arrow D: is twisted, the flow of the flow medium passing over ^; . the rear edge of the viewing wave will increase and result in a slight tilting of the button, as illustrated in Fig. 4 '. The effects of these processes are in ^; the force diagram shown in Pig "5, in which the pressure build-up and pressure drop across the pressure"; The piece area is shown as »f ', ι

Because of these effects, it is desirable to form the print or the surface so that this unwanted tilting of the pressure piece or the surface can be corrected "

In FIGS. 8 and 9, the simplest button design is illustrated. Basically, this design falls over the pressure piece surface 5ö with a recess 57 and a raised circular threshold 58, which are shown more clearly in FIG. 9, which is a sectional view along the line IX-IX in FIG ₄ 8 is. The head part 50 of the button is wider than the cylindrical lower part 01 »which sits in the pocket 36. Pressurized flow medium is fed through the passage 3 '·· (or 40j, and the filter 5h to the mouth 55 of the head arrangement 35. From the interior of the button lower part, the flow medium passes through the throttle opening 59 into the recess 57, Ve im so in the As the pressure increases through passage 38, the pressure acting on the runner formed by surface 34 increases, thereby absorbing the increased compressive loads exerted on pressure ring 32 via the pressure plate assembly, and so on.

! Since the button moves back and forth in his pocket axial sighting, the pressure from the

Ί gang 38 (or 4üj, with which the underside of the button is

t is hit, endeavors to press the button on the pressure surface 34 for the optimal space between the threshold and the pressure surface for the pressures occurring and the best storage by the hydrostatic film. By: this arrangement, the effects are both thermal ^ ^s and the mechanical twisting forces considerably ver _~: ί »Ringert Furthermore, the hydros tatisohen button on stock;? mechanical bearings interacting with them for the partitioning |

ι ■ ■ ■ *.

009831/1074

.200U8-4

the pushbuttons are tuned to solve the problems the over- and over-the-counter compensation is barred to a minimum can become »by the sublime threshold is provided in the middle on the printing surface, 'becomes the hydrodynamic Druekaufb.au Un the leading edge of the pressure surface of the button 'increases, creating a. favorable tilting of the button is provoked «, The use of a tilted Button (surface force - higher than hub force at full pressure in the recess) with a flow restriction to reduce 'the pressure in the' recess creates a stable arrangement that is able to withstand changes in the pressure profile over the area of the button when the speed changes new and to compensate for changes in the oil viscosity. If the If the button is too far away from the pressure plate, the pressure in the recess drops, so that the button is reset again * When the button tries to touch the pressure plate, the pressure in the recess increases and separates the two Surfaces. .

In the fig-, 6 and? Another printing area for button 35 is illustrated, FIG. 7 being a sectional view taken along line VII-VII in FIG. In this embodiment, multiple thresholds are used, the above mentioned hydrodynamic effects weaken, Aue Figures "6 and 7 it can be seen that the pressure surface comprises an outer smaller circular sill 60 having a plurality of sipes 61 which extends in connection with an internal end hat ΐ> 2 stand. This smaller threshold does not create a bearing, but it is followed by a concentric outer larger threshold 63, which is followed by a uuten-shaped recess 64 and then a concentric inner larger threshold 65, an annular recess 57 being arranged in the center of the pressure surface. Only the groove-shaped recess 64

00983t / 1074

200H84

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receives a supply of pressurized flow medium through inner passages 6 b, and the oil penetrating into the central recess 57 can drain off via passages 67 and 68. By this arrangement, the force diagram is changed by being distributed by the Mttelbereieh of the knob in ring-like pattern in the seal on the outer diameter _0, since the relatively narrow "force ring" endeavors same hydrodynamic pressure buildup au seineu diametrically opposite sides to have, it endeavors to stabilize the button and to reduce the tilting of the pot »

It is evident that "the arrangements discussed above the bearing ii? and 13 help the buttons to stabilize the pressure plate assembly and an additional one Cause storage if the buttons do not fully compensate or overcompensate for the axial pressure loads, especially in the case of high angles of vision in the aggregate Aatür- Layers 12 and 13 take radial component 31 the inclined printer lifts without the support of the button. in stock.

009831/1074

Claims (1)

PATENT CLAIMS 1.) Hydrostatic pressure bearing device for a hydraulic axial piston unit with a pressure plate arrangement rotatably mounted in the unit and several connecting rods mounted in the pressure plate arrangement, the hydrostatic pressure bearing device being located between the unit and the pressure plate arrangement in order to absorb the pressure forces exerted by the connecting rods on the Druckplattenanordriung are exercised, characterized by a plurality of pockets (36, 37), which are arranged in the unit at the height of the printing plate assembly and - around its circumference, passages (38, 39, ^ 0, 41), each pocket with a Connect source for pressurized flow mfidiufflon, several individual button bearings (35) > each of which sits in a pocket "and has axial freedom of movement and freedom of tilting movement, and each of which includes a bearing pressure surface (56)? which has a central recess (57) which, in connection with the source for ^^ pressurized flow medium in the zugeqrdnetJen Patent Attorneys DipL-lng. Mariin L · idί { _ί Dipl; -Wirtsch.Wng / Ax ^ Hαnsm Jasehe stands, as well as a raised circular threshold (58), and a washer-like rotor surface (32) cooperating with the thrust bearings, which the thrust plate assembly is assigned and rotates with this and is arranged parallel to the bearing surfaces of the individual button bearings, so that the pressurized flow medium in the pockets the associated thrust bearing in the direction of the rotating Runner surface presses to compressive loads on the pressure plate assembly to be accommodated in a large number of individual hydrostatic bearings 2 "Hydrostatic Drueklagereinriehtung according to claim 1, characterized in that the pressure plate arrangement is rotatably mounted on roller bearings (12, 13) and the hydrostatic Thrust bearing arrangement cooperates with the roller bearings to compensate for pressure loads « 3. Hydrostatic Drueklagereinriehtung according to claim 1, characterized in that the pockets are circular ulind— bores which are formed in the iüJrper of the hydraulic unit near the circumference of a radial flange (18j au the Druekplatteuanordnung, whereby axial pressure loads through the in the pockets seated button surface fc can be compensated ₀ h _e Hydrostatic Drueklagereinriehtung according to claim 1, characterized in that a are uruppe the fascheu (36) connected to a common passage which is in ■ fluid communication with one side of the hydraulic ■ 'assembly, and the other group of the bags to a common, separate passage connected; which is in fluid communication with the other side 'of the hydraulic unit, so that one group 'of the pockets has the inlet side of the unit as a source of pressurized flow medium, while the other 009831/1074 200 H84 Group of pockets use the outlet side of the unit as a source of pressure medium Has. 5. jiydrostatic thrust bearing device according to claim k _f, characterized in that the two groups of pockets are arranged in a semicircle with a common Dimekmittelquelle. 6. Hydrostatic Druokiagereinrichtuug "according to claim 1, characterized in that the pressure or bearing surface of each individual IC button bearing has an outer, smaller circular threshold (6 (3) which does not bear any load and is provided with outlet notches (61), -sowie · an outer and an inner circular threshold (63 and 65) between which there is a pressurized circular recess, and that the bearing surface of each button bearing has a central recess (57) with a passage (6,7) for eng Discharge of the flow medium from the central recess is provided. 7. A hydrostatic button for the formation of a bearing between rotating surfaces with desirable tilting shafts for improved hydrostatic bearing; characterized by a pocket in one of the surfaces with a source of pressurized fluid and a button (35) in the Pocket is axially arranged and has axial freedom of movement and freedom of tilting movement, the button having an outer, smaller, no-load circular sill that is designed with drainage cuts, an outer and an inner circular sill with an interposed, pressurized recess, a central recess with a passage for the discharge of S-trommigsmedium from the central recess and a second passage between the bag and the pressurized circular Äusnelimung on we i st "- ■ '.. 0098 3 i / 10 Blank page