CS201256B1

CS201256B1 - Device for metering the losses between the piston and cylinder of the axial hydrostatic converter

Info

Publication number: CS201256B1
Application number: CS585577A
Authority: CS
Inventors: Vladimir Galba
Original assignee: Vladimir Galba
Priority date: 1977-09-08
Filing date: 1977-09-08
Publication date: 1980-10-31

Description

Vynález sa týká zariadenia na meranie strát medzi piestom a valcom axiáineho hydrostatického prevodníka.The present invention relates to a device for measuring losses between a piston and a cylinder of an axial hydrostatic transducer.

Na základe poznatkov získaných rozborom súčasného stavu merania třecích strát medzi piestom a valcom axiáineho hydrostatického prevodníka sa javí, že uvedené meranie sa prevádza na zariadení vytvorenom experimentálnym modelom, regulacným hydrostatickým prevodom a pomocnými hydraulickými obvodmi. Experimentálny model sa skládá z náhonu so šikmou doskou uloženou vo valivých ložiskách, z jedného pista s kízadlom a s púzdra uloženého v meranom válci, ktorý je uložený v dvoch radiálnych hydrostatických ložiskách a ktorý má eliminované axiálně sily od hydrostatického tlaku kva2 paliny vo válci. Ďalšou častou experimentálneho modelu je dvojpolohový rozvádzač zabezpečujúci striedanie tlaku vo válci. Rozvádzač je poháňaný excentrom cez pevný převod od náhonu. Priebeh změny tlaku vo válci je upravený akumulátormi. Pomocné hydraulické obvody sa skladajú z napájecieho obvodu meraného valca s hydrogenerátorom a prepúšťacími ventilmi, z napájacieho obvodu hydrostatického ložiska ' meraného valca vytvořeného hydrogenerátorom a prepúšťacím ventilom a z viacerých odsávacích čerpadiel na odsávanle prietokových strát. Z tohoto zariadenia sa získavajú óscilografické záznamy časového priebehu axiálnej a tangenciálnej trecej sily medzi piestom a valcom. Trecia strata W sa potom vyhodnocuje z oscilografických záznamov podlá vztahu.Based on the knowledge obtained by analyzing the current state of friction loss measurement between the piston and the cylinder of the axial hydrostatic transducer, it appears that said measurement is carried out on a device created by an experimental model, a control hydrostatic transmission and auxiliary hydraulic circuits. The experimental model consists of an inclined plate drive mounted in rolling bearings, a pendulum with a pendulum and a housing mounted in a measured cylinder, which is mounted in two radial hydrostatic bearings and which has eliminated axial forces from the hydrostatic pressure of the quartz in the cylinder. Another part of the experimental model is a two-position distributor providing pressure alternation in the cylinder. The distributor is driven by an eccentric via a fixed transmission from the drive. The course of pressure change in the cylinder is adjusted by accumulators. The auxiliary hydraulic circuits consist of the feed circuit of the metered cylinder with the hydrogen generator and bypass valves, the feed circuit of the hydrostatic bearing of the metered cylinder formed by the hydrogenator and the bypass valve, and a plurality of suction pumps at the flow loss suction. From this device, oscillographic records of the time course of the axial and tangential frictional forces between the piston and the cylinder are obtained. The friction loss W is then evaluated from the oscillographic records according to the relationship.

HH

kde F_ta= axiálna trecia silawhere F _t a = axial frictional force

F_TT= tangenciálna trecia sila ds = elementárny zdvih piesta H = celkový zdvih piestaF _TT = tangential friction force ds = elementary piston stroke H = total piston stroke

Nevýhodou popísaného zariadenia sú poměrně rozsiahle hydraulické obvody, nevhodnost použitia pre experimentovanie pri vyšších tlakoch a otáčkách prevodníka, obtiažnosť dosiahnutia požadované] teploty pracovnej kvapaliny z dovodov značnej netěsnosti celého experimentálneho modelu, poměrně velká spotřeba energie pre pohon experimentálneho modelu a pre pohon vysokotlakového hydrogenerátora. Naviac a] sa^ motné získavanie konečných výsledkoch merania z oscilografických záznamov uvedeným matematickým postupom je velmi zdíhavé a predlžuje čas potřebný na riešenie problému.Disadvantages of the described device are relatively extensive hydraulic circuits, unsuitability for experimentation at higher pressures and speed of the converter, difficulty in achieving the required temperature of the working fluid due to considerable leakage of the whole experimental model, relatively high energy consumption for driving the experimental model and for high-pressure hydrogenator. Moreover, obtaining the final measurement results from the oscillographic recordings by said mathematical procedure is very time-consuming and prolongs the time needed to solve the problem.

Uvedené nevýhody znižuje zariadenie ha meranie strát medzi piestom a valcom axiálneho hydrostatického prevodníka pozostávajúce z expe. rimentálneho modelu, tvořeného prvým snímačom, snímajúcim axiálně trecie sily, druhým snímačom, snímajúcim tangenciálně trecie sily a talokom, ktorý je spojený s náhonom a uzatvorený rozvádzacím vekom, podlá vynálezu, ktorého podstata spočívá v tom, že blok sa skládá z válcovitého telesa, v ktorom sú axiálně umiestnené dva rovnoběžné otvory, z ktorých v prvom je upevněné púzdro hydrostatického ložiska, v ktorom je uložený meraný válec s meraným púzdrom, v ktorom je uložený meraný piest a v druhom je vytvořený priestor pre pomocný válec, v ktorom je uložené pomocné puzdro s pomocným piestom, pričom meraný piest a pomocný piest sú cez kízadlá v styku so šikmou doskou pevne spojenou s hriadefom, s ktorým je spojený kotúč, v ktorom je vytvořená kulisa pre fotočlánok, spojený cez třetí přenosový kanál s počítacím blokom, ku ktorému sú cez přenosové kanály připojené snímače, pričom rozvod tlakového média k meranému valcu a pomocnému valcu je převedený nátrubkom a kanálom, na ktorý sú napojené napájecie kanále pre privádzanle tlakového média cez rozvod vytvořený v púzdre k hydrostatickému ložisku, pričom prepojenle pracovných priestorov meraného pies. ta a pomocného piesta je převedené rozvádza^ cím kanálom, na ktorý je nátrubok a kanál napojený.The aforementioned disadvantages are reduced by the device h and the loss measurement between the piston and the cylinder of the axial hydrostatic transducer consisting of the expe. The experimental model of the first transducer sensing the axial frictional forces, the second transducer sensing the tangentially frictional forces and the talc connected to the drive and closed by the distributor lid, according to the invention, characterized in that the block consists of a cylindrical body. which are axially positioned two parallel holes, in the first of which is fixed the bush of the hydrostatic bearing, in which the measured cylinder with the measured housing is stored, in which the measured piston is stored, and in the second is created space for the auxiliary cylinder, with the auxiliary piston, the measured piston and the auxiliary piston being in contact with the inclined plate fixedly connected to the shaft to which the disc in which the photocell is formed is connected via the wings, connected to the counting block via a third transmission channel to which they are transmitted channels connected sensors, where the distribution of pressure The pressure medium to the measured cylinder and the auxiliary cylinder is transferred through a sleeve and a channel to which the supply channels for supplying the pressure medium are connected through a distribution formed in the housing to the hydrostatic bearing, interconnecting the working spaces of the measured sand. The piston and the auxiliary piston are transferred through a distribution channel to which the sleeve and the channel are connected.

Zariadenie na meranie strát medzi piestom a valcom axiálneho hydrostatického prevodníka umožňuje spol'ahlivejšie a presnejšie meranie třecích a prietokových strát pri vyšších otáčkách a tlakoch, čo je nutnou podmlenkou pre zabezpečenle inovácle. Prevedenie celého zariadenia aj samotného experimentálneho modelu sa zjednodušuje a podstatné sa znižuje spotřeba energie na pohon experimentálneho modelu a na výrobu tlakovej kvapaliny aj na jej chladenie. Zariadenie lepšie modeluje podmienky prevodníka z hladiska teploty kvapaliny a mazania konca piesta. Bez změny nastavenia pracovných parametrov sa možu súčasne merať straty pri generátorovom aj pri motorovom režime, čo umožňuje v krátkom čase previesť vačší počet merani.The device for measuring the losses between the piston and the cylinder of the axial hydrostatic transducer enables more reliable and accurate measurement of frictional and flow losses at higher speeds and pressures, which is a necessary condition for a secure innovation. The design of the whole device and the experimental model itself is simplified and the energy consumption for driving the experimental model and for the production of pressurized liquid and its cooling is significantly reduced. The device better simulates the conditions of the transducer in terms of liquid temperature and piston end lubrication. Without changing the operating parameter settings, losses in both generator and motor mode can be measured simultaneously, allowing more measurements to be made in a short time.

Na připojených výkresoch je znázorněný prí. klad prevedenia zariadenia pre meranie strát medzi piestom a valcom axiálneho hydrostatického prevodníka podlá vynálezu, kde na obr. 1 je znázorněný pozdížný rez experimentálnym modelom ako aj schématicky znázorněné prepojenie snímačov a fotočlánku s počítacím blokom a na obr. 2 prevedenie kotúča, v ktorom je vytvořená kulisa pre fotočlánky.In the accompanying drawings, FIG. an embodiment of a device for measuring the losses between the piston and the cylinder of an axial hydrostatic transducer according to the invention, wherein in FIG. 1 shows a longitudinal section through an experimental model as well as a schematic representation of the connection of the sensors and the photocell to the counting block; and FIG. 2 shows an embodiment of a roll in which a backdrop for photocells is formed.

Zariadenie na meranie strát medzi piestom a valcom axiálneho hydrostatického prevodníka je vytvořené z experimentálneho modelu, ktorý je jednak cez hrladel' 12 spojený s kotúčom 7, v ktorom je vytvořená kulisa 71 pre fotočlánok 8 a jednak opatřený prvým snímačom 5 na snímanie axiálnej trecej sily a druhým snímačom 6 na snxmanie tangenciálnej trecej sily. Prvý a druhý snímač 5, 6 je cez prvý a druhý přenosový kanál 51, 61 spojený s počítacím blokom 9, ku ktorému je připojený pomocou tretieho přenosového kanála 81 fotočlánok 8. Samotný experimentálny model je vytvořený náhonom 1, blokom 2 a rozvádzacím vekom 4. Náhon 1 sa skládá zo skrlne 11, v ktorej je na ložiskách 13 uložený hriadef 12, ktorého vstupná časť je utesnená rotačným těsněním 14. Na hriadeli 12 je naklinovaná šikmá doska 15. Blok 2 sa skládá z válcovitého telesa 21, v ktorom sú axiálně umiestnené dva rovnoběžné otvory. Prvý je pre puzdro 22 hydrostatického ložiska 24, v ktorom je uložený meraný válec 251 s meraným púzdrom 28 a meraným piestom 271. Druhým otvorom je vytvořený priestor pomocného valca 252, v ktorom je uložené pomocné púzdro 23 s pomocným piestom 272. Meraný piest 271 a pomocný piest 272 sú opatřené klzadlami 28 kízne uloženými na šikmej doske 15. Přívod kvapaliny do meraného valca 251 je zaistený cez nátrubok 29 a do pomocného valca 252 cez kanál 30, na ktorý sú napojené napájecie kanále 31 určené na napájenie hydrostatického ložiska 24, pričom rozvod kvapaliny k hydrostatickému ložisku 24 je realizovaný cez púzdro 22, v ktorom je hydrostatické ložisko 24 uložené. Na hydrostatické ložisko 24 je pomocou připojovacích častí připojený prvý snímač 5 a druhý snímač B. Na pbvod prietokových strát z hydrostatického ložiska 24 slúži prvý odvádzací kanál 32. Prietokové straty, ktoré vzniknú netesnosťou okolo nátrubku 29, sa odvádzajú druhým odvádzacím kanálomThe device for measuring the losses between the piston and the cylinder of the axial hydrostatic transducer is formed from an experimental model, which is connected via a shaft 12 to a disc 7, in which a slide 71 for the photocell 8 is formed and secondly provided with a first sensor 5 for sensing axial frictional force; a second transducer 6 for sensing the tangential frictional force. The first and second sensors 5, 6 are connected via a first and second transmission channel 51, 61 to a counting block 9, to which a photocell 8 is connected via a third transmission channel 81. The experimental model itself is formed by a drive 1, a block 2 and a distribution lid 4. The drive 1 consists of a housing 11 in which a shaft 12 is mounted on the bearings 13, the inlet part of which is sealed by a rotary seal 14. The shaft 12 has a sloped plate 15. The block 2 consists of a cylindrical body 21 in which they are axially positioned two parallel holes. The first is for the housing 22 of the hydrostatic bearing 24, in which the measured cylinder 251 with the measured housing 28 and the measured piston 271 is accommodated. The second opening is formed by the auxiliary cylinder space 252 in which the auxiliary housing 23 is stored. the auxiliary piston 272 is provided with slide slides 28 on a sloping plate 15. The liquid supply to the measured cylinder 251 is provided through the sleeve 29 and to the auxiliary cylinder 252 through a channel 30 to which the feeding channels 31 are connected for feeding the hydrostatic bearing 24. of the fluid to the hydrostatic bearing 24 is realized through a housing 22 in which the hydrostatic bearing 24 is received. The first sensor 5 and the second sensor B are connected to the hydrostatic bearing 24 by means of the connecting portions. The first drain channel 32 is provided for the flow losses from the hydrostatic bearing 24. The flow losses generated by the leak around the sleeve 29 are drained by the second drain channel.

33. Rozvádzacie veko 4 sa skládá z rozvádzacieho telesa 41, v ktorom sa nachádza rozvádzací kanál 42 a z konzoly 43 slúžiacej na upnutie prvého snímača 5. Pohon experimentálneho modelu je zaistený regulačným pohonom, ku ktorému sa može podlá potřeby přiradit redukčný převod. Tlakovou kvapalinou sa experimentálny model napája rozvádzacím kanálom 42 cez prvé potrubie 36 od hydrogenerátora. Kvapalina na udržovanie pracovnej teploty v skříni 11 sa přečerpává čerpadlom cez druhé potrubie 37. Prietokové straty medzi meraným valcom 251 a meraným piestom 271 umožňuje merať tesniaci pripravok 34 upevněný na čele hydrostatického ložiska 24 a napojený na odvádzacie potrubie 35, ktoré slúži na odvod únikovej kvapaliny k odmernému zariadeniu. Medzi expepimenálnym modelom a regulačným pohonom je umiestnený kotúč 7, v ktorom je vhodné vytvořená kulisa 71 pre fotočlánok 8 určený na vytváranie riadlaceho signálu S_R.33. The distributor cover 4 consists of a distributor body 41 in which the distributor channel 42 is located and a bracket 43 for holding the first sensor 5. The drive of the experimental model is provided by a control drive, to which a reduction gear may be associated as required. Pressurized fluid feeds the experimental model through the distribution channel 42 through the first conduit 36 from the hydrogen generator. The fluid for maintaining the working temperature in the housing 11 is pumped through the pump via the second conduit 37. The flow losses between the measured cylinder 251 and the measured piston 271 allow to measure the sealing device 34 mounted on the face of the hydrostatic bearing 24 and connected to the discharge conduit 35 to the measuring device. A disc 7 is disposed between the expepimal model and the control drive, in which a slide 71 for a photocell 8 designed to produce a control signal S _R is suitable.

Samotné meranie sa prevádza tak, že hydrogenerátorom sa v prvom potrubí 38 při nastavenom ventile vytvoří požadovaný tlak. Pohonom sa experimentálnemu modelu udelia potřebné o. táčky a v pracovnom priestore skrine 11 sa pomocou termostabilizačného obvodu napojeného na skriňu 11 druhým potrubím 37 nastaví požadovaná teplota. Meraný piest 271 a pomocný piest 272 sú posobením tlaku kvapaliny na ich če.lá pritláčané cez kízadlá 28 na šikmú došku 15. Otáčaním šikmej došky 15 sa piestom udělí axiálny pohyb, pričom tlaková kvapalina sa prevádza z pracovného priestoru meraného piestaThe measurement itself is carried out in such a way that the hydraulic generator generates the desired pressure in the first conduit 38 with the valve set. Propulsion will give the experimental model the necessary o. the desired temperature is set by means of a thermostabilizing circuit connected to the housing 11 via the second conduit 37. The measured piston 271 and the auxiliary piston 272 are subjected to the pressure of the liquid on their faces pressed through the sliders 28 on the inclined thatch 15. By rotating the inclined thatch 15, the piston is axially moved, the pressure fluid being transferred from the working space of the measured piston.

271 do pracovného priestoru pomocného piesta271 into the auxiliary piston workspace

272 a naopak podlá směru ich pohybu, ktorý je fázovo natočený o 180°. Rozvádzacím kanálom 42 sa z hydrogenerátora doplňuje len kvapalina potřebná na krytie prietokových strát okolo meraného piesta 271, pomocného piesta 272, pod klzadlami 28, okolo telesa hydrostatického ložiska 24 a okolo nátrubku 29, čo umožňuje dosiah,nuť rovnoměrný odběr tlakovej kvapaliny. Hydrostatické ložisko 24 je účinkom tlakovej kvapaliny oddělené od púzdra 22 olejovým filmom a všetky trecie sily medzi meraným piestom 271 a meraným púzdrom 26 sa prenášajú na prvý snímač 5 pre snímanie axiálnej trecej sily Sa a na druhý snímač 6 pre snímanie tangenciálnej trecej sily S_T. Otáčením kotúča 7 opatřeného kulisou 71 pre fotočlánok 8 sa vytvára riadiaci signál S_R) ktorý nám umožňuje určit krajné polohy meraného piesta 271 a pomocného piesta 272 ako aj frekvenciu ich axiálneho pohybu. Tieto signály sa privádzajú do počitacieho bloku 9 odkial' po ich spracovaní sa získá výstup, určujúci hodnotu relatívnej trecej straty podl'a skór uvedeného matematického vztahu upraveného na následovný tvar:272 and vice versa according to the direction of their movement, which is rotated 180 °. Only the fluid required to cover the flow losses around the measured piston 271, the auxiliary piston 272, under the sliders 28, around the hydrostatic bearing body 24 and around the sleeve 29 is supplied from the hydrogenator duct 42 to allow for uniform pressure fluid withdrawal. The hydrostatic bearing 24 is separated from the housing 22 by an oil film under pressure and all frictional forces between the measured piston 271 and the measured housing 26 are transmitted to the first sensor 5 for sensing the axial frictional force Sa and to the second sensor 6 for sensing the tangential frictional force S _T. By rotating disk 7 provided the backdrop for photocell 71 8 creates a control signal S _R) allows us to determine the extreme positions of the measured piston 271 and the auxiliary piston 272 and the frequency of their axial movement. These signals are fed to the counting block 9 from where, after processing, an output is obtained determining the relative frictional loss value according to the scores of said mathematical equation adjusted to the following form:

^WR ^W R

CJCJ

Sp sin CJ tdt + k‘ _v2 sinCJt dtSp sin CJ tdt + k ' _at 2 sinCJt dt

F _TT ^FTA kde W_R = relativná trecia strata — o = kruhová frekvencia rotačného pohybu hriadefa náhonuF _TT ^F TA where W _R = relative friction loss - o = circular frequency of rotary motion of drive shaft

Sp = činná plocha meraného piesta F_ta = axiálna trecia sila F_TT - tangenciálna trecia sila k = konstanta experimentálneho modelu t = priebežný čas ti - čas medzi dvomi krajnými polohami piestaSp = effective area of the measured piston F _t a = axial frictional force F _TT - tangential frictional force k = constant of the experimental model t = running time ti - time between two extreme positions of the piston

ΓΑΓΑ

Pohyb měrného piesta 271 s frekvenciou ω při nastavenom tlaku p smerom von z meraného púzdra 26 považujeme za motorový režim a pri zasúvaní meraného piesta 271 do meraného púzdra 26 hovoříme o generátorovom režime. Pri nastavenom plniacom tlaku sú tieto režimy opačné. Celková relativná trecia strata W_R je potom súčet relatívnej trecej straty pri pracovnom tlaku a relatívnej trecej straty pri plniacom tlaku dvou odpovedajúcich režimov. Vyhodnocoyanie relatívnej trecej straty zanedbává striedanie pracovného a plniaceho tlaku počas jed-Movement of metering piston 271 with frequency ω at set pressure p out of the measured housing 26 is considered as a motor mode and when inserting the measured piston 271 into the measured housing 26 we are talking about the generator mode. At the pre-set pressure, these modes are reversed. The total relative frictional loss W _R is then the sum of the relative frictional loss at the working pressure and the relative frictional loss at the feed pressure of the two corresponding modes. The evaluation of the relative friction loss neglects the alternation of working and filling pressure during one

Claims

201256 the plunger 272 is a plurality of fluid pressure applied to the plunger through the skins 28 to the sloping plate 15. By rotating the inclined ramp 15, the piston is axially moved, whereby the pressurized fluid is transferred from the working piston of the measured piston 271 to the working space of the auxiliary piston 272 and vice versa according to the direction of movement which is phased 180 °. Only the liquid and the necessary to cover the flow losses around the metered piston 271, the auxiliary piston 272, the slipper 28, around the body of the hydrostatic bearing 24 and around the sleeve 29 are supplied by the distribution channel 42 to the pump to achieve an even pressure fluid withdrawal. The hydrostatic bearing 24 is due to the pressure fluid separated from the housing 22 by an oil film and all frictional forces between the measured piston 271a and the measured housing 26 are transmitted to the first sensor 5 for sensing the axial friction force and the second sensor 6 for sensing the tangential thrust ST. By rotating the disc 7 provided with the photocell cage 71, a control signal SR is formed which allows us to determine the extreme positions of the measured piston 271 and the auxiliary piston 272 as well as the frequency of their axial movement. These signals are fed to the counting block 9f after their processing, the output is determined to determine the value of the relative friction loss according to the corrected mathematical relationship provided by the following shape: WR CJ 2 Sp sin CJ tdt + k '1 v2 sinCJt dt F TT —- - FTA where WR = relative friction loss - o = circular frequency of the rotational movement of the drive shaft Sp = the effective surface of the measured piston = the axial friction of the silaFTT - the tangential frictional silak = the constant of the experimental modelut = the running time ti - the time between the two extreme positions estaΑ Movement of the measuring piston 271 With the frequency ω of the set pressure p outwards of the measured housing 26, we consider it to be the engine mode and the engagement of the measured piston 271 into the measured housing 26 is referred to as a generator mode. The total relative friction loss WR yet the sum of the relative frictional loss at the work pressure and the relative friction loss at the filling pressure of the two corresponding modes. The evaluation of the relative friction loss neglects the shooting of the working and filling pressure during the subject.

A device for measuring losses between a piston cylinder of an axial hydrostatic transducer, consisting of an experimental model consisting of a first sensor sensing axial thrust, a second sensor sensing a tangentially frictional force, and a block that is coupled to a drive and closed by a distribution lid, characterized by in that the block (2) comprises a cylindrical body (21) in which two parallel openings are axially disposed, the first of which is a housing (22) of the hydrostatic bearing (24) in which the caliper (251) is housed with the measured housing (26) in which the measured piston (271) is housed and in the second space provided for the auxiliary cylinder (252), in which the auxiliary housing (23) is disposed with the plunger 1272), and the measured piston (271) and the auxiliary piston (272) is via sliders (28), in contact with the inclined plate (15), of a rigidly coupled cycle, as is the case with a real converter. R, however, at the specific time courses of Fta and FTTs, comes to the conclusion that the error caused by this simplification is much less than 1percento. The flow losses are measured in the static state with minimal movements of the measured point 271 only to avoid the influence of the exposure by measuring the leakage liquid discharged from the sealant 34 through the discharge line 35 to the metering device. of the invention with a shaft (12) with which a disk (7) is coupled to which a slide (71) for the photocell (8) is formed, connected via a third transfer channel (81) to a counting block (9) to which through the transducer channels (51, 61) of the connected sensor (5, 6), wherein the pressure medium distribution to the measured cylinder (251) and the auxiliary cylinder (252) is transferred through the sleeve (29) and the channel (30), on which connected feed channels (31) for supplying pressure medium through the manifold formed in the housing (22) to the hydrostatic bearing (24), the connection of the working areas of the measured position (271) and the auxiliary piston (272) being transmitted to the distributor a channel (42) to which the tube (29) and the channel (30) are connected.

2. Apparatus according to claim 1, characterized in that the inclined plate (15) is located in a sealed working space formed by the housing 201256 (11), to which a thermostabilization circuit is connected via a second pipe (37).

3. Apparatus according to claim 1, characterized in that the measured piston (271) is guided through a sealing means (34) which is mounted on the face of the hydrostatic bearing (24) and connected to the discharge line (35). 2 drawings