EP0043881A1 - Mit mehreren synchronisierten Arbeitsräumen ausgestattetes rotationshydraulisches Gerät zum Umformen und Verteilen - Google Patents

Mit mehreren synchronisierten Arbeitsräumen ausgestattetes rotationshydraulisches Gerät zum Umformen und Verteilen Download PDF

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Publication number
EP0043881A1
EP0043881A1 EP19800401063 EP80401063A EP0043881A1 EP 0043881 A1 EP0043881 A1 EP 0043881A1 EP 19800401063 EP19800401063 EP 19800401063 EP 80401063 A EP80401063 A EP 80401063A EP 0043881 A1 EP0043881 A1 EP 0043881A1
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EP
European Patent Office
Prior art keywords
displacements
stator
pressure
radius
active
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP19800401063
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English (en)
French (fr)
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EP0043881B1 (de
Inventor
Gaston Sauvaget
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Individual
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Individual
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Priority to EP19800401063 priority Critical patent/EP0043881B1/de
Priority to DE8080401063T priority patent/DE3071830D1/de
Publication of EP0043881A1 publication Critical patent/EP0043881A1/de
Application granted granted Critical
Publication of EP0043881B1 publication Critical patent/EP0043881B1/de
Expired legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/08—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/356—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C2/3566—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along more than one line or surface

Definitions

  • the invention relates to a hydraulic distributor-distributor device with synchronized multi-displacement intended to transform hydraulic energy into kinetic energy of rotation and vice versa.
  • the known solutions / motors or hydraulic pumps do not make it possible to obtain both a high number of gear ratios and good efficiency. Their pressure / mass power / torque ratio is unfavorable. Their lifespan is generally short due to the significant internal forces which they generate. Their performance is particularly low in small reports because they circulate a large volume of inactive hydraulic fluid.
  • the uses of hydraulic motors of known type are currently technologically limited in power, the maximum displacement developed to date is of the order of 20 liters.
  • This type of engine does not support the elastic deformations of organs, ovalizations, dimensional variations due to temperature differences, because they generate abnormal forces which cause very rapid wear as well as significant leaks reducing power and efficiency. Their proper functioning requires very fine surface finishes as well as very large metallic masses to limit leaks due to elastic deformations.
  • the device according to the invention aims to overcome these drawbacks.
  • the invention as characterized in the claims solves the problem of creating a hydraulic device making it possible to obtain very large direct torques at low speed, capable of reaching the limits of current technology, that is to say say of the order of 1,000,000 da.Nm and this with a mass that is relatively smaller as the torque increases, therefore with increasing mass power It offers the possibility of self-compensating for dimensional variations which whatever its origin, producing very few leaks without causing wear or cyclic pulsations. Its overall displacement can range from the fraction of a liter to hundreds of liters with very many speed ratios in both directions of rotation with remarkable efficiency.
  • the advantages obtained thanks to this invention consist essentially in that the very large torques are obtained by simple variation of the mean radius of the displacements R 1 - r: 2; the section of application of the working fluid being able to remain constant by ranges of couples.
  • the device is in the form of a substantially rectangular cross-section consisting of a set of concentric rings, namely: a distributor cam or stator in which are formed recesses acting as displacements delimited by the internal radius R1 of the rotor and . by the sealing flanges mounted on bearings.
  • the engine torque is obtained via the average radius of the displacements Rm which can reach several meters, in cooperation with the number of active displacements and the number of active valves in these displacements.
  • the flow rate of the working fluid is preferably constant, but it can however allow a variation of the order of 15% for the change of gears.
  • the admission of the working fluid is controlled separately for each displacement or pair of displacements in radial opposition, the inactive displacements are not subjected to a flow of fluid and remain completely pained without absorbing any power.
  • the valves are designed with a differential section to be controlled with double effect by the controlled admission of the high pressure fluid (of the order of 250 bar) into the active displacements. This arrangement allows self-compensation for dimensional variations, ovalizations, etc., particularly for large diameters because the valves are continuously kept in contact under pressure on the active parts of the displacements, radius r.
  • the speeds are obtained by combining the active displacements. When all the displacements are active, we have the highest torque and the lowest speed, when only the smallest displacement is active and receives all of the working fluid remained constant, we have the lowest and highest engine torque rotor rotation speed. Freewheeling takes place by instantly making all displacement inactive.
  • the device according to the invention comprises 4 equidistant displacements A, B, C, D, formed in the stator 1 of external radius R.
  • the bottom of each of the cylinders is of radius r a , r b ' r c , r d .
  • the rotor concentric with the stator 1 has a large clearance J between the radius R and the radius R internel rotor.
  • the rotor has 24 equidistant and radially oriented grooves 3, in which 24 differential valves 4 slide.
  • the closing flanges are assembled by 24 bolts 5.
  • Each of the ramps has a groove Ru, for the displacement A these grooves are designated by Ru 1 , Ru 2 , etc. In these grooves terminate the intake and exhaust ducts of working fluid 10. These ducts act, according to the direction of rotation, as a function of intake or exhaust of the fluid. Here, the direction of rotation is represented by the arrow F.
  • the lines 10 have been designated by HP for high pressure and BP for low pressure. In the inactive displacement B, all the conduits are in BP.
  • a valve 12 is shown descending the ramp R a2, while another valve 13 goes up the ramp R al .
  • a displacement is limited by the pre-active valves located on either side thereof. In fig.l, the displacement is defined by the valves 14 and 15, the valve 16 is no longer tight on R.
  • the two grooves Ru of each displacement are of length equal to that of the ramps or preferably a little longer as in fig. 2.
  • the edge of the valve 4 is at the end of the cylindrical part r however the edge of the groove Rua is located opposite the pressure exchanger duct of the valve which is therefore defused, that is to say - say made inactive. This allows the valve to go up the boom in equipression. It is the same for the valve 12 which descends the ramp. The construction details of the valves will be described later.
  • FIG. 3 there is shown the section along AA of fig.l.
  • the reference numbers in fig. 1 and 2 have been used.
  • This view shows the section of the torus constituting the annular device, the shape of the stator 1, of the rotor 2, of the closing flanges 17,18, and of the roller bearings 19,20, as well as their retaining flange 21,22, fixed by screws 23 on the flanges 17,18.
  • Static seals 24 and rotational seals 25, 26 ensure the tightness of the assembly.
  • the circulation of the fluid at the pressure Pi of the casing is represented by a shading with small points. We also see the differential return chambers 7 of the valves.
  • Figure 4 shows the section along BB of fig.l.
  • the circulation of the fluid at the pressure of the casing is also represented by a shading with small points.
  • This view also shows the fixing of the flanges 17,18 on the rotor 2 by means of the bolts 27.
  • the holes 28 (fig.3) and 29 (fig.4) have a centering and a tapping, they are used for fixing on the built on the one hand and on the receiving member on the other.
  • Fig.5 shows the valve in elevation. It is in the form of a rectangular parallelepiped whose differential section is obtained by making a shoulder 30, 31, on the short sides, which has the effect of reducing the surface 32 of the underside or valve head relative to the upper surface 33 on which the working fluid acts to make the valve slide in its housing by crossing said valve through the holes 34,35,36,37 (fig.8) drilled from the face 33 and opening into a longitudinal groove of slight depth 38 located on the axis of symmetry YY of the face 32.
  • the valve has on its axis of symmetry XX a tapped hole 39 which receives a threaded sleeve 40 (valve 12 in fig.2) limiting the stroke of the pusher 41 recalled by the spring 42 in the output position.
  • the function of this plunger is to make the valve pre-active on the radius R of the stator in the absence of a defusing pressure in the differential chambers, so as to automatically delimit the active displacements when the valves pass.
  • the differential return pressure of the valves in the bottom of their housing must be greater than the thrust of the return springs 42 so that the output end of the pusher 41 is almost completely inserted into the socket 40, which has the effect of preventing the valve from coming into watertight contact on the spoke R.
  • the valves are furthermore each provided with a plating clearance 43 of shallow depth, situated on each of their large parallel faces in the part of the valve always remaining inside the housing in the rotor; this clearance opens at 44 on the face 32.
  • This face 32 is of concave shape along a radius 45 (fig.12) R + r which corresponds to the mean radius Rm of the displacements .
  • This radius Rm is connected to the large external faces by a flat or better by a convex part 46, 47, being in contact with the ramps Ru at the time of the descent or of the rise of the valves in the displacements.
  • the valves are also provided with pressure exchanger pipes 48,49, fig.10,11, each putting one of the surface portions 32 into communication with the clearance 44 located on the opposite face.
  • the depth of the displacements R - r is preferably different, in particular when they are three in number or multiples of three or 2. They are of equal depth in pairs in diametric opposition, each pair may or may not be different from the others in volume..
  • the cylindrical parts R of the stator, of developed length L and r of developed length 1 must be of substantially equal length and of a value such that they allow each to receive at least two valves simultaneously.
  • the different reduction ratios or speeds can be obtained according to a Renard series, by successively combining displacements of different or equal volume, the volume of which is calculated as a function of this progression.
  • At least one of the displacements can be used as a pump, compressor or distributor to control or control auxiliary functions or one or more displacements of a second device operating in parallel or in series with the first.
  • the invention applies to all cases of coupling, decoupling, distribution and conversion of power, speeds, torques, for small, medium, large and very large powers.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
EP19800401063 1980-07-15 1980-07-15 Mit mehreren synchronisierten Arbeitsräumen ausgestattetes rotationshydraulisches Gerät zum Umformen und Verteilen Expired EP0043881B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP19800401063 EP0043881B1 (de) 1980-07-15 1980-07-15 Mit mehreren synchronisierten Arbeitsräumen ausgestattetes rotationshydraulisches Gerät zum Umformen und Verteilen
DE8080401063T DE3071830D1 (en) 1980-07-15 1980-07-15 Rotary hydraulic converting and distributing device with multiple synchronized cylinders

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19800401063 EP0043881B1 (de) 1980-07-15 1980-07-15 Mit mehreren synchronisierten Arbeitsräumen ausgestattetes rotationshydraulisches Gerät zum Umformen und Verteilen

Publications (2)

Publication Number Publication Date
EP0043881A1 true EP0043881A1 (de) 1982-01-20
EP0043881B1 EP0043881B1 (de) 1986-11-12

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EP19800401063 Expired EP0043881B1 (de) 1980-07-15 1980-07-15 Mit mehreren synchronisierten Arbeitsräumen ausgestattetes rotationshydraulisches Gerät zum Umformen und Verteilen

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EP (1) EP0043881B1 (de)
DE (1) DE3071830D1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0609820A1 (de) * 1993-02-04 1994-08-10 Robert Bosch Gmbh Flügelzellenpumpe

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113244741B (zh) * 2021-04-27 2022-11-08 湖北灏瑞达环保能源科技有限公司 一种废气处理喷淋塔用液体收集用再分布器

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191202340A (en) * 1911-02-25 1912-08-29 Edgar Flygh Girod Improvements in and relating to Steam-engines of the Rotary Type.
US2396316A (en) * 1942-04-02 1946-03-12 Houdaille Hershey Corp Hydraulic pump or motor
US2873683A (en) * 1956-06-05 1959-02-17 Farmingdale Corp Floating non-sticking blades
US3139036A (en) * 1961-09-14 1964-06-30 Daniel F Mcgill Rotary piston action pumps
GB986172A (en) * 1961-12-23 1965-03-17 Beteiligungs & Patentverw Gmbh Hydraulic torque converter
US3241456A (en) * 1962-12-26 1966-03-22 Baron C Wolfe Rotary fluid motor
US3416457A (en) * 1966-07-19 1968-12-17 Applied Power Ind Inc Vane type fluid converter
US3450004A (en) * 1967-06-06 1969-06-17 Biasi Charles P De Auto-kinetic wheel or fluid motor
FR2057272A5 (de) * 1969-08-08 1971-05-21 Sauvaget Gaston
AU443618B2 (en) * 1969-05-14 1973-12-10 Leonard Haffner Thomas Rotary motors or pumps

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191202340A (en) * 1911-02-25 1912-08-29 Edgar Flygh Girod Improvements in and relating to Steam-engines of the Rotary Type.
US2396316A (en) * 1942-04-02 1946-03-12 Houdaille Hershey Corp Hydraulic pump or motor
US2873683A (en) * 1956-06-05 1959-02-17 Farmingdale Corp Floating non-sticking blades
US3139036A (en) * 1961-09-14 1964-06-30 Daniel F Mcgill Rotary piston action pumps
GB986172A (en) * 1961-12-23 1965-03-17 Beteiligungs & Patentverw Gmbh Hydraulic torque converter
US3241456A (en) * 1962-12-26 1966-03-22 Baron C Wolfe Rotary fluid motor
US3416457A (en) * 1966-07-19 1968-12-17 Applied Power Ind Inc Vane type fluid converter
US3450004A (en) * 1967-06-06 1969-06-17 Biasi Charles P De Auto-kinetic wheel or fluid motor
AU443618B2 (en) * 1969-05-14 1973-12-10 Leonard Haffner Thomas Rotary motors or pumps
FR2057272A5 (de) * 1969-08-08 1971-05-21 Sauvaget Gaston

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0609820A1 (de) * 1993-02-04 1994-08-10 Robert Bosch Gmbh Flügelzellenpumpe

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Publication number Publication date
DE3071830D1 (en) 1987-01-02
EP0043881B1 (de) 1986-11-12

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