US3584984A - Rotary device - Google Patents

Rotary device Download PDF

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Publication number
US3584984A
US3584984A US793412*A US3584984DA US3584984A US 3584984 A US3584984 A US 3584984A US 3584984D A US3584984D A US 3584984DA US 3584984 A US3584984 A US 3584984A
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US
United States
Prior art keywords
blades
piston
casing
inlet
rotor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US793412*A
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English (en)
Inventor
Julian Franciszek Majkowski
Zdzislaw Ryszard Przybylski
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZAKLADY MECHANIZZNE TARROW
Original Assignee
ZAKLADY MECHANIZZNE TARROW
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Filing date
Publication date
Priority claimed from PL125557A external-priority patent/PL62603B1/pl
Application filed by ZAKLADY MECHANIZZNE TARROW filed Critical ZAKLADY MECHANIZZNE TARROW
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Publication of US3584984A publication Critical patent/US3584984A/en
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Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/20—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with dissimilar tooth forms
    • 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
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/18—Control of, monitoring of, or safety arrangements for, machines or engines characterised by varying the volume of the working chamber

Definitions

  • a rotary expansible chamber device having a casing of primarily circular cross section modified by peripherally spaced pockets of circular cross section; a rotary piston in the primary circular cross section of the casing has blades radially extending therefrom of epicycloidal shape, the tips of which are closely adjacent the primary surface of the casing. Cylindrical locks in each pocket are rotated synchronously with the piston and have recesses which receive the blade tips.
  • Inlet passages extend from the hollow center of the piston through the rear faces of the blades, and outlet passages extend through the front faces of the blades to the hollow center of the piston, the hollow piston center being divided into inlet and outlet spaces.
  • the piston is axially shiftable to vary the-working chamber volume.
  • the working and thermal machines generally are of great weight and large dimensions, and performance indices of the given machine, such as the unit power, unit weight, flow intensity in relation to design capacity, are not always favourable and are very limited in a great many cases.
  • the active element i.e. the rotor or the rotational piston
  • the active element when revolving also has a circling motion about the axis of the main shaft which action requires for its accomplishment that cranks or planetary gearings be used.
  • cranks or planetary gearings be used.
  • Rotary devices today in use are also characterized in that they can only rarely be used for other purposes than those they have been intended.
  • a gear pump, Encke pump, vane type or a Lysholm pump, or Roots, Wade and Vickers compressors in the capacity of a hydraulic motor of a gas engine, they must be significantly redesigned to meet the newly posed requirements.
  • the Hartmann" hydraulic motor may be, for instance, considered for use as a pump, or compressor, but it would be rather difficult to employ this motor in the capacity of an internal combustion engine.
  • the known rotary devices generally are distinguished by characteristic properties of the volumetric type working machinery or engines without simultaneously exhibiting the specific advantages of the flow-type machinery, such as rotodynamic pumps and compressors or turbines.
  • the Wankl, Radziwill, Rozycki orthe Weinberger machines are primarily volumetric type machines.
  • the Encke pump, gear pumps, sliding-vane and screw-type pumps and compressors, and the Roots compressors exhibit certain features of the flow-type machines. These features are, however, not too many, reference being made to the absence of suction and delivery valves and also the fact that the suction and delivery action is a continuous process.
  • the Marshall internal combustion engine when considered from this point of view, if found to have additionally such features as a high operating speed and dynamic balance of the revolving elements however, the intensity of flow in this engine due to the relatively small ratio of the working volume to the design volume, and the l-lartmann" engine because of the low-speed characteristics and small design volume, is not comparable with that produced in the rotodynamic pumps and compressors or turbines.
  • suction and delivery do not represent a continuous, but a partly intermittent process, which is so because the suction passage is closed ofi by the broad ends of the rotor lugs, and in the case of Hartmann engines-there are the rotational locks on the rotor circumference that close off the inlet and the outlet ports.
  • the rotary device comprises a piston rotor having on its periphery radial blades in the form of epicycloidally contoured teeth which mate with recesses in rotating cylindrical locks which recesses provide an envelope of the successive locations of the blade apex edges, so that these teeth function as pistons; also, the piston rotor is centrally mounted in a casing being seated in bearings and has rotary motion only the cylindrical locks are coupled kinematically to the piston rotor and remain in tight cooperation therewith, which locks are also mounted by way of bearings in sockets spaced radially on the periphery of the casing thus dividing the design volume of this device into any desired number of separate spaces.
  • the device is built just as discussed above with the only difference being that the piston rotor is slidably mounted on a hollow shaft with a sleeve mating therewith and provided with a suitable socket capable of accommodating the piston rotor and with inlet or outlet passages, whereby the piston rotor may slide in or out of the corotating sleeve thus changing its active width.
  • the inlet and outlet passages are provided in the hollow shaft communicating with the working spaces and opening to the suction or delivery side of the piston-rotor blades, or in the case of the alternative device modification the inflow of the medium to the working spaces proceeds through the hollow shaft and then further via the piston rotor, whereas the outflow takes place by way of passage provided in the sleeve which rotates together with the rotor, or vice versa.
  • These passages can be also disposed in a quite different way. It is, on the other hand, very important that in both these modifications there exists geometrical contact the rotor blades mating with the cavities of the cylindrical locks, which contact is simultaneously effected along three generating lines common for both the rotor blade and lock recess i.e. along the two lock recess edges and the rotor blade apex, this contact being a result of kinematics of the mating elements and their epicycloidal contours.
  • the active element such as the piston rotor mounted on the hollow shaft and the cylindrical locks have only rotary motion because of which the inside faces of the casing do not have a complex shape, the piston rotor and the cylindrical locks are completely dynamically balanced, and no pressures occur on the mating surfaces of these elements since their contact is purely geometrical.
  • the hollow shaft may even be of the same diameter as the piston rotor, rotational speed of the latter being only limited by strength, are of the or drive takeoff aspects and allowable maximum rate of medium flow, and in case of internal combustion engines by the combustion rate.
  • Sealing of the mating elements is made by the so-called "small gap" which is sufficient if the peripheral speed of the piston rotor is adequately selected and the pressure differences between neighboring working chambers are not very large; irrespective of the above this seal may be also provided in any other convenient manner.
  • the rotary device as disclosed herein operates also as a piston machine which means that the suction and compression or delivery action takes place due to volumetric changes in the working chambers being, at the same time, a continuous process as in typical flow machines, like rotodynamic compressors and pumps or turbines and some other known rotary devices, as for instance vane pumps or sliding-vane type compressors.
  • this device has also some other characteristic properties typical for the flow-type machines, like a very wide range of rotational speeds, a high uniformity of these speeds, exceptionally large flow intensities, which properties are comparable only with those characteristic for rotodynamic pumps and compressors or turbines of the same capacity.
  • the device according to this invention is also notable for its self-control ability with regard to the internal compression ratio according to the actual operating conditions, one of its modifications providing also the possibility of continuous control of flow intensity, efficiency or rotational speed with a very wide range of adjustment.
  • this device satisfies the condition of full universality under the most diversified applications, being used as one or more modifications of the hereinbefore mentioned working machines and engines.
  • This is possible with small alterations introduced in the method of the feed-in and feed-off systems of the flow medium, and with plural the discussed devices combined into one integrated assembly, each of them being mounted on a common shaft and hence kinematically coupled, or else mounted separately and gas-or hydrodynamically coupled, or built also in other different combinations as an integral part of a set consisting of a compressor, piston turbine and variable-speed transmission or hydraulic motor.
  • FIG. 1 is a half elevation and half-section view of the device ofthe present invention which may be used as a compressor;
  • FIG. 2 is a cross-sectional view; taken on line A-A of Fig. 1
  • FIG. 3 is a longitudinal cross section of a modification of this device which may be used for instance as a pump or hydraulic motor;
  • FIG. 4 is a cross-sectional view taken along lines A-A; 8-H; and C-C ofFIG. 3.
  • the rotary device as herein disclosed may be used as a compressor, pump, hydraulic motor or gas engine and comprises a primarily cylindrical ribbed casing l in which a piston rotor 3 is centrally located on a hollow shaft 2 and is peripherally fitted with blades 4 having the form of teeth which are epicycloidal in their contours and with generating lines parallel or skew in relation to the centerline of said hollow shaft 2.
  • the blades 4 mate with cavities 5 made in the form ofa recess to receive the epicycloidal tooth in the cylindrical locks 6 mounted parallel to the hollow shaft 2 in peripherally spaced sockets 8 on the casing 1.
  • the ribbed casing l is closed at.
  • Casing 1 has a hollow in which is located a separating piece 15 dividing this space into two parts; the inlet space 16 and the outlet space 17 which are sealed by means of gasket 18 and gland 19.
  • the inlet space 16 communicates via passages 20 with the rear part of radial blades 4 rotation of piston rotor 3 being clockwise in FIG. 2, while the outlet space 17 communicates via passages 21 with the front part of these radial blades 4, both said passages, Le.
  • FIGS. 3 and 4 The modification of the device according to this invention capable of fulfilling the function of a variable-delivery pump, compressor, gas engine or hydraulic motor is shown in FIGS. 3 and 4, wherein there is a casing 24 closes by front cover 25 and rear cover 26, in which there is mounted in bearings 27 and 28 the hollow shaft 29 seated centrally in relation to casing 24 and carrying a piston rotor 30 slidably mounted thereon and fitted with radial blades 31 made in the form of epicycloidally contoured teeth mating tightly with the cavities 32 made in the cylindrical locks 33, locks 33 are mounted on shafts 34 and are located by bearings 35 and 36 in sockets 37 parallel to the hollow shaft 29 and disposed radially on the peripheries of casing 24.
  • the front part of the radial blades 31 of appertaining to piston rotor 30 is connected by passages 43 in said sleeve 38 to an annular space 44 in the front cover 25 and further to outlet 45.
  • On the opposite side of said sleeve 38 just behind the piston rotor 30 seated on the hollow shaft 29 there is mounted slidably a push rod 46 which under the a fluid pressure medium fed by way of port 47 moves the piston rotor 30 inside the sleeve 38 thus diminishing the active width of the piston rotor 30.
  • Fluid pressure medium fed by port 48 pushes the pistonrotor 30 out of sleeve 38.
  • Kinematic coupling of the hollow shaft 29 carrying the piston rotor 30, and the shafts 34 carrying the cylindrical locks 33 is effected by means of gear wheels 49 and 50.
  • the suction side is separated in the working spaces, on the one hand, by the apex edge of the rotor blades 3 or 30 travelling along the internal surface of easing l or 24, or along the inside surface of cavities 5 or 32 of the cylindrical locks 6 or 33, and on the other hand, by the linear contact of the outside surfaces of the cylindrical locks 6 or 33 with those of the piston rotor 3 or 30, or else by the linear contact of the edge of cavities 5 or 32 of the cylindrical locks 6 or 33 with the outer surfaces of rotor blades 4 or 31.
  • This separation is, at the same time, a seal for the suction side.
  • a continuous regulation of the intensity of flow is in such a way achieved within very wide operating limits, while in the case of a hydraulic motor or gas engine operating in a closed-loop system with a constant-delivery pump or compressor a wide possibility of rotational speed control is created, too.
  • the device according to this invention as an internal combustion engine in a variety of modifications, and in particular a modification where the compressor is connected with the decompressor (gas engine) by way of suitable combustion chambers and some alterations are made in the feed and exhaust systems; each unit of such an assembly is operating on the principle as described before.
  • the combination of the compressor and decompressor may be implemented in a number of ways, as mentioned before.
  • the herespecified exemplary embodiments of the rotary device according to this invention do not exhaust all the feasible design potentialities which may add much to the subject invention by developing it still further.
  • the kinematic coupling of the rotor shaft and lock shafts may be achieved by means of an assembly of friction wheels and other types of transmission; the movement of the rotor in relation to sleeve may be implemented by a mechanical or pneumatic method, while the inlet and outlet passages can be made so as to bypass the rotor shaft and form a system of adequate interstices.
  • the above-mentioned method of combining said devices into sets or bigger assemblies, capable of fulfilling various functions, by no means exhaust all the variant potentialities.
  • a rotary expansible chamber device comprising: a casing having a primarily cylindrical cross section and a plurality of peripherally spaced parallel sockets, piston rotor means coaxially rotatably mounted in said casing and comprising a plurality of generally radially extending blades, cylindrical lock means rotatably mounted in each said socket having recess means for receiving said blades as said rotor means and lock means rotate, inlet passage means extending from a fluid inlet through the rear face of each said blade, and outlet passage means extending through the front face of each said blade to a fluid outlet.
  • blades are of epicycloidal contour.
  • the rotary expansible chamber device of claim 1 and further comprising means mounting said blades for axial movement relative to said lock means, and means for axially moving said blades.
  • a rotary expansible chamber device comprising:
  • a casing having a primarily cylindrical cross section and a plurality of peripherally spaced parallel sockets
  • piston rotor means coaxially rotatably mounted in said casing and comprising a plurality of generally radially extending blades
  • cylindrical lock means rotatably mounted on in each said socket having recess means for receiving said blades as said rotor means and lock means rotate,
  • passage means for introducing fluid rearwardly of each blade and for removing fluid from forwardly of each blade
  • said blades each having an epicycloidal contour.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
US793412*A 1968-02-03 1969-01-23 Rotary device Expired - Lifetime US3584984A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
PL12489268 1968-02-03
PL125557A PL62603B1 (de) 1968-03-01

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US3584984A true US3584984A (en) 1971-06-15

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US793412*A Expired - Lifetime US3584984A (en) 1968-02-03 1969-01-23 Rotary device

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US (1) US3584984A (de)
DE (1) DE1904339A1 (de)
FR (1) FR2001276A1 (de)
GB (1) GB1253884A (de)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3780710A (en) * 1970-10-22 1973-12-25 Z Przybylski Rotary internal-combustion engine
US4145168A (en) * 1976-11-12 1979-03-20 Bobby J. Travis Fluid flow rotating machinery of lobe type
US5738065A (en) * 1996-08-30 1998-04-14 Linnel; Jean Variable rotary engine
US6868822B1 (en) * 1999-07-15 2005-03-22 Engineair Pty Ltd Rotary piston engine
US20090308347A1 (en) * 2008-06-16 2009-12-17 P.R.E.C. Planetary rotary engine
US20110303184A1 (en) * 2010-06-11 2011-12-15 Usher Meyman Internal combustion engine
US20120285415A1 (en) * 2010-09-11 2012-11-15 Pavel Shehter Internal combustion engine with direct air injection
US20150132167A1 (en) * 2008-04-10 2015-05-14 Fritz Forgy Rotary pump or motor with orbital piston aspiration, methods of production and uses thereof
JPWO2013137337A1 (ja) * 2012-03-14 2015-08-03 国立大学法人 名古屋工業大学 ローター・セット、内燃機関、流体ポンプ、流体圧縮機、および機械
US20180038339A1 (en) * 2015-02-17 2018-02-08 Mitsubishi Heavy Industries, Ltd. Water flow power generator
US10145243B2 (en) 2013-11-06 2018-12-04 Planetary Rotor Engine Company Planetary rotary engine with rotary ring valves
US10683755B2 (en) 2017-06-26 2020-06-16 Pdt, Llc Continuously variable turbine
WO2020145808A1 (ru) * 2019-01-10 2020-07-16 Зуфар Хурматуллович ГАЙДУЛЛИН Роторно-лопастной двигатель

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH627528A5 (de) * 1977-09-07 1982-01-15 Bbc Brown Boveri & Cie Oelpumpe, insbesondere schmieroelpumpe fuer turbomaschinen.

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US958416A (en) * 1909-12-27 1910-05-17 George A Metcalf Rotary steam-engine.
US1269735A (en) * 1916-03-11 1918-06-18 Frederick H Ogden Rotary steam-engine.
US1272876A (en) * 1915-01-11 1918-07-16 James Wallace Tygard Balanced reversing rotary engine.
US1751843A (en) * 1929-06-05 1930-03-25 Rosett Joshua Air compressor
US2483705A (en) * 1941-09-16 1949-10-04 Keelavite Co Ltd Rotary engine, pump, and the like
US2963981A (en) * 1957-03-11 1960-12-13 Hanastsuka Tadashi Variable discharge rotary pump
US3112677A (en) * 1962-02-09 1963-12-03 Hartmann Mfg Company Hydrodynamic unit

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US958416A (en) * 1909-12-27 1910-05-17 George A Metcalf Rotary steam-engine.
US1272876A (en) * 1915-01-11 1918-07-16 James Wallace Tygard Balanced reversing rotary engine.
US1269735A (en) * 1916-03-11 1918-06-18 Frederick H Ogden Rotary steam-engine.
US1751843A (en) * 1929-06-05 1930-03-25 Rosett Joshua Air compressor
US2483705A (en) * 1941-09-16 1949-10-04 Keelavite Co Ltd Rotary engine, pump, and the like
US2963981A (en) * 1957-03-11 1960-12-13 Hanastsuka Tadashi Variable discharge rotary pump
US3112677A (en) * 1962-02-09 1963-12-03 Hartmann Mfg Company Hydrodynamic unit

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3780710A (en) * 1970-10-22 1973-12-25 Z Przybylski Rotary internal-combustion engine
US4145168A (en) * 1976-11-12 1979-03-20 Bobby J. Travis Fluid flow rotating machinery of lobe type
US5738065A (en) * 1996-08-30 1998-04-14 Linnel; Jean Variable rotary engine
US6868822B1 (en) * 1999-07-15 2005-03-22 Engineair Pty Ltd Rotary piston engine
US20150132167A1 (en) * 2008-04-10 2015-05-14 Fritz Forgy Rotary pump or motor with orbital piston aspiration, methods of production and uses thereof
US8356585B2 (en) * 2008-06-16 2013-01-22 Planetary Rotor Engine Company Planetary rotary engine
CN102124196A (zh) * 2008-06-16 2011-07-13 行星旋转引擎公司 行星旋转发动机
US20090308347A1 (en) * 2008-06-16 2009-12-17 P.R.E.C. Planetary rotary engine
US20110303184A1 (en) * 2010-06-11 2011-12-15 Usher Meyman Internal combustion engine
US20120285415A1 (en) * 2010-09-11 2012-11-15 Pavel Shehter Internal combustion engine with direct air injection
US8613269B2 (en) * 2010-09-11 2013-12-24 Pavel Shehter Internal combustion engine with direct air injection
JPWO2013137337A1 (ja) * 2012-03-14 2015-08-03 国立大学法人 名古屋工業大学 ローター・セット、内燃機関、流体ポンプ、流体圧縮機、および機械
US10145243B2 (en) 2013-11-06 2018-12-04 Planetary Rotor Engine Company Planetary rotary engine with rotary ring valves
US20180038339A1 (en) * 2015-02-17 2018-02-08 Mitsubishi Heavy Industries, Ltd. Water flow power generator
US10215150B2 (en) * 2015-02-17 2019-02-26 Mitsubishi Heavy Industries, Ltd. Water flow power generator
US10683755B2 (en) 2017-06-26 2020-06-16 Pdt, Llc Continuously variable turbine
WO2020145808A1 (ru) * 2019-01-10 2020-07-16 Зуфар Хурматуллович ГАЙДУЛЛИН Роторно-лопастной двигатель

Also Published As

Publication number Publication date
DE1904339A1 (de) 1969-09-04
GB1253884A (en) 1971-11-17
FR2001276A1 (de) 1969-09-26

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