US3885897A - Lubricating device for radial sealing strips of inner-axial rotary piston engines of trochoidal construction with sliding engagement - Google Patents

Lubricating device for radial sealing strips of inner-axial rotary piston engines of trochoidal construction with sliding engagement Download PDF

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Publication number
US3885897A
US3885897A US379601A US37960173A US3885897A US 3885897 A US3885897 A US 3885897A US 379601 A US379601 A US 379601A US 37960173 A US37960173 A US 37960173A US 3885897 A US3885897 A US 3885897A
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United States
Prior art keywords
lubricant
pumps
sealing strip
engine
pump
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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
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US379601A
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English (en)
Inventor
Franz Huf
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Dornier System GmbH
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Dornier System GmbH
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Filing date
Publication date
Priority claimed from DE19722240100 external-priority patent/DE2240100C3/de
Application filed by Dornier System GmbH filed Critical Dornier System GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
    • 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
    • F01C21/04—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F02B2053/005—Wankel engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2730/00—Internal-combustion engines with pistons rotating or oscillating with relation to the housing
    • F02B2730/01—Internal-combustion engines with pistons rotating or oscillating with relation to the housing with one or more pistons in the form of a disk or rotor rotating with relation to the housing; with annular working chamber
    • F02B2730/018—Internal-combustion engines with pistons rotating or oscillating with relation to the housing with one or more pistons in the form of a disk or rotor rotating with relation to the housing; with annular working chamber with piston rotating around an axis passing through the gravity centre, this piston or the housing rotating at the same time around an axis parallel to the first axis
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to a lubricating device for the radial sealing strips of inner-axial rotary piston engines of trochoidal construction with sliding engagement.
  • the sealing strips were positioned more or less loosely in their sealing strip beds in the housing.
  • the sealing strips were moreover unlubricated and dry, which did not lead to the most favorable oper ating conditions, and which affected both the gas sealing and the wear and tear of the sealing strip material.
  • a lubricant supply into the sealing strip bed alone is unsatisfactory because it is primarily the round surface of the sealing strip which is to have a closed lubricating film within its contact range, being dependent on the pivot angle, with the piston sliding past. This is not assured with a general lubricant supply into the sealing strip bed.
  • the supply of lubricant is advantageously dosed or metered greater on the rising or running-up side of the radial sealing strip than on the descending or running-down side thereof.
  • the supply, or delivery, of the lubricant may take place simultaneously both at the running-up and at the runningdown side of the sealing strip, but it is advantageous that the supply be effected alternately on one side and then on the other side of the radial sealing strip.
  • each of the two mutually oppositelypositioned ends of each a sliding bar or linkage may be utilized as the piston of such a lubricant pump.
  • one of the two thus formed lubricant pumps is advantageously connected with the oil grooves of the running-up side of the radial sealing strips, and the other lubricant pump is connected with the oil grooves of the running-down side of the radial sealing strips.
  • FIG. 1 schematically illustrates a two-chambered rotary piston engine with the basic provision of the lubricating device and the arrangement of the lubrication lines or piping;
  • FIGS. 2a and 2b illustrate the radial sealing strip arrangement on an enlarged scale
  • FIG. 3 illustrates one construction of a lubricant pump
  • FIG. 4 illustrates a modified embodiment of FIG. 3
  • FIGS. 50 and 5b are cross-sectional views taken along line A-A and line A-B-CD-E-A, respectively, of FIG.
  • FIG. 5c is a cross-sectional view taken along line A-A of FIG. 1 after the rotation of the piston through an angle of FIG. 6a is a cross-sectional view taken along line F-F of FIG. I;
  • FIG. 6b is a cross-sectional view showing a modified embodiment of the structure of FIG. 6a.
  • FIGS. 1, 5 and 6 illustrate, in a greatly simplified manner, the housing I of a rotary piston engine.
  • This engine comprises two working chambers and, correspondingly, two combustion chambers, also not further identified.
  • the piston 2 has a trochoidal configuration and rotates in the direction of the arrow.
  • the wall of the housing I constitutes the outer envelope curve branches with respect to the trochoidal piston 2.
  • What is involved, therefore, is an engine with a sliding engagement and two contraction points of the housing at which points the radial sealing strips 4 are located.
  • the piston center M executes a circle 3 about the central point M
  • the rotational movement may be produced in any desired manner. Selected in this case is a construction which does not utilize conventional gearing, but an eccentric control instead.
  • Such an eccentric gear is known per se.
  • Provided for the two axial directions 1: and y is one guide ring each 6.1: and 6y, respectively, together with a disc rotatably positioned therein.
  • Coordinated to both discs is an eccentric 5 whose center coincides with the trochoid center M,.
  • the eccentric 5 carries the piston 2 and is non-rotatably connected thereto.
  • the eccentric shaft EW of the engine rotatably extends through the eccentric 5.
  • the two guide rings 6): and 6y are displaceable in the x-direction and in the ydirection together with the discs mounted therein. The displaceability and the slide bars necessary for this purpose are shown in FIG. 1 for the x-direction.
  • FIGS. 5a, b and c show slide bars 7y and 7y for the y-direction.
  • the slide bars 7 and 7' of the guide gear are utilized as the pistons of the lubricant pumps 8 and 8'.
  • the mutually corresponding elements of the left and of the right slide bar and pump have been identified in the drawing with the same reference numerals, difi'ering however in the sign.
  • the guide gear with the lubricant pumps 8 and 8' mounted thereon is positioned laterally outside of the lateral housing wall, as illustrated by pump housing sections la and 1b of housing 1 in FIG. 6a, and does not obstruct the piston movement in any way. For this reason, the elements of the guide gear have been shown in dashed and dash-dotted lines. For each of the lubricant pumps 8 and 8' one inflow line 9 and 9' is present.
  • Feed lines 10 and 10 extend from the lubricant pumps by way of non-return valves 11 to the distributing lines for the lubricant.
  • the lubricant pump 8 conveys the lubricant by way of the feed line 10 to the two distributing lines 12a and 12b which supply in each case, via a non-return valve 11, the running-up or rising side of the radial sealing strips 4 with lubricant.
  • the lubricant pump 8' supplies, by way of the distributing line 12a and 12b, equally via non-return valves 11, the running-down or descending sides of the radial sealing strips 4.
  • the non-return valves 11 are positioned in each case closely ahead of the oil grooves of the radial sealing strips 4.
  • the oil grooves themselves have been merely indicated in FIG. 1 in the sealing strip bed.
  • the lubrication of the sealing strip 4 is effected from the oil grooves through the gap 4a for the rising or running-up side, and through the gap 4b for the running-down or descending side.
  • the rising side of the sealing strips 4 is supplied with lubricant.
  • the descending side of the sealing strip 4 is lubricated.
  • the lubrication of the rising and of the descending sides takes place alternately. It is also possible to lubricate both sides simultaneously.
  • FIG. 6b shows a modified pump P which is mounted in a manner which makes it more readily replaceable.
  • pump P is provided with pump chamber 80 which is in communication with and forms an extension of the chamber of pump 8.
  • Slide bar extension 70 is attached to slide bar 7 and slides in chamber 8c of pump P.
  • FIG. 1 It is shown in FIG. 1 that the running-up or rising sides of all the sealing strips 4 are lubricated simultaneously. It is also possible, however, to effect the lubrication of the individual sealing strips successively.
  • one sealing strip could be lubricated by the slide bar illustrated, coordinated to the guide ring 6x and the pump 8, whereas the other sealing strip 4 could be supplied by an analogously constructed lubricant pump coordinated to the guide ring 6y.
  • other pump types also may be used without difficuity, provided they are guided or controlled by the rotating eccentric shaft. In the case of the guide or control by means of the eccentric shaft, separate control means for the lubricant pumps are eliminated in a simple manner.
  • the construction and provision of the lubricating device described herein is not limited to the use in two-chambered rotary piston engines but is usable, of course, also for rotary piston engines whose construction is based on other trochoids and which have more working chambers.
  • FIGS. 2a and 2b illustrate in different views and at an enlarged scale the provision of the oil grooves in the sealing strip bed.
  • the radial sealing strip 4 is guided in its sealing strip bed within the housing 1.
  • the oil grooves 41 and 42 Disposed at the two lateral flanks of the sealing strip bed are the oil grooves 41 and 42. They extend over the entire length of the radial sealing strip 4 and project to the outside through the lateral housing wall 1'.
  • a non-return valve 11 Positioned immediately ahead of the oil groove 42 is also a non-return valve 11. By way of this non-return valve and the distributing lines, the fine oil groove is in connection with one of the two lubricant pumps 8 or 8', which have not been illustrated in detail here.
  • the delivery or supply of the lubricant to the fine oil grooves 41 and 42 also make take place in any other manner.
  • the lubrication proper of the radial sealing strip 4 is effected from the oil groove 41 by way of a narrow gap 40 to the rising side of the sealing strip.
  • the descending side of the sealing strip 4 is supplied with lubricant from the oil groove 42 through a corresponding narrow gap 4b between the housing and the sealing strip.
  • FIG. 3 illustrates the two end portions of the guide gear with the slide bars 7 and 7'.
  • the lubricant pumps formed therefrom have again been identified with ref erence numerals 8 and 8', as in FIG. I.
  • the guide ring 6x has been omitted.
  • the slide bar 7 is shown here in one end position, and this end position for the lubricating pump 8 corresponds specifically to one dead center (UT) position.
  • the other end position namely the other dead center (OT) position, has been shown in dash-dotted lines.
  • the entire stroke H between the two positions corresponds to four times the eccentricity of the rotary piston engine, i.e.
  • the entire stroke H is not absolutely required, but for example, the part h, suffices for the dosage or metering.
  • the dosage results from the arrangement of the inflow line 9.
  • the working stroke h, between the inflow line 9 and the OT position determines the quantity fed.
  • the lubricant is further fed through the line 10 in the direction of the arrow.
  • a different position of the inflow line for example 9' in FIG. 3, at a shorter distance k from the cylinder end in the lubricant pump 8', a smaller quantity is fed.
  • FIG. 4 illustrates a different arrangement for dosing or metering the lubricant in a longitudinal and crosssectional view thereof.
  • the slide bar of the guide gear again constitutes a piston having an associated cylinder with the connecting feed line 10.
  • the lubricant is conveyed by an inflow line 9 at any desired point within the UT position and distributed through an annular groove 9a ove the circumference of the cylinder. From the annular groove 9a axial grooves 8a extend in the direction toward the end of the lubricant pump 8.
  • grooves 8a terminate at a distance from the cylinder end, and from the OT position, which corresponds to the effective working stroke h or 11 .
  • the lubricant is again forced back through the inflow line 9. Only that part of the lubricant which has collected in the pumps after the closing-off of the inflow lines 9 or the grooves 8a in the area h or 11 is conveyed via the line for the lubrication proper.
  • a rotary piston engine having a piston means of epitrochoidal configuration, a housing having an internal configuration conforming substantially to the outer envelope curve of the trochoid, eccentric shaft means operatively connected to said piston, radial sealing strip means mounted in a corresponding bed in the interior side walls of said housing and lubricant groove means formed in the walls of said bed, the improvement comprising, drive means operatively connected to said piston to convert linear sliding movement of said drive means to rotary motion of said piston, pump means operatively coupled to at least one sliding element of said drive means, lubricant line means operatively connecting said pump means to said lubricant groove and nonreturn valve means operatively mounted in said lubricant line.
  • An engine in accordance with claim 1 which includes means for supplying an increased quantity of lubricant to the lubricant groove on the running-up side of the sealing strip.
  • the lubricant line means includes a pair of lubricant line means, one of which is connected to the lubricant groove means in the bed on one side of the sealing strip means and the other of which is connected to the lubricant groove means in said bed on the other side of said sealing strip and said pump means alternately supplies lubricant to said lubricant groove on said one side of said sealing strip through said one lubricant line means and to said lubricant groove on said other side of said sealing strip through said other lubricant line means.
  • the lubricant line means includes a pair of lubricant line means, one of which is connected to all lubricant groove means in the beds on the running-up sides of said sealing strips and the other of which is connected to all lubricant groove means in said beds on the running-down sides of said sealing strip means and said pump means alternately supplies lubricant to said lubricant grooves on said running-up side of said sealing strips through said one lubricant line means and to said lubricant grooves on said running-down side of said sealing strips through said other lubricant line means.
  • the lubricant line means includes a pair of lubricant line means, one of which is connected to the lubricant groove means in the bed on the running-up side of the sealing strip and the other of which is connected to the lubricant groove means in said bed on the runningdown side of said sealing strip
  • the pump means includes a pair of pump means, one of which is connected to the lubricant line means leading to said running-up side of said sealing strip and the other of which is connected to the lubricant line means leading to said running-down side of said sealing strip.
  • the pump means includes a pair of pumps, a pair of input lubricant line means is provided, one of which is connected to one of said pumps and the other of which is connected to the other of said pumps, and said input lubricant line means are connected to said pumps at different distances from the dead-center position of the pistons of said pumps, whereby the lubricant output of said pumps differs.
  • the pump means includes a pair of pumps, axially extending grooves are provided in the walls of each of said pumps, a pair of input lubricant line means is provided, one of which terminates in said grooves in said wall of one of said pumps and the other of which terminates in said grooves in said wall of the other of said pumps, and said grooves in said walls of each of said two pumps terminate at different distances from the dead-center position of the piston of the respective pumps, whereby the lubricant output of said pumps differs.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Rotary Pumps (AREA)
  • Reciprocating Pumps (AREA)
US379601A 1972-08-16 1973-07-16 Lubricating device for radial sealing strips of inner-axial rotary piston engines of trochoidal construction with sliding engagement Expired - Lifetime US3885897A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19722240100 DE2240100C3 (de) 1972-08-16 Schmiereinrichtung für Dichtleisten einer parallel- und innenachsigen Rotationskolbenmaschine

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US3885897A true US3885897A (en) 1975-05-27

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US379601A Expired - Lifetime US3885897A (en) 1972-08-16 1973-07-16 Lubricating device for radial sealing strips of inner-axial rotary piston engines of trochoidal construction with sliding engagement

Country Status (7)

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US (1) US3885897A (enrdf_load_stackoverflow)
JP (1) JPS4963812A (enrdf_load_stackoverflow)
FR (1) FR2196666A5 (enrdf_load_stackoverflow)
GB (1) GB1419322A (enrdf_load_stackoverflow)
IT (1) IT990125B (enrdf_load_stackoverflow)
NL (1) NL7309596A (enrdf_load_stackoverflow)
SE (1) SE380583B (enrdf_load_stackoverflow)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3994637A (en) * 1974-08-16 1976-11-30 Dornier System Gmbh Rotary piston engine of trochoidal design
US5295814A (en) * 1989-10-04 1994-03-22 Archimedes Associates Inc. Trochoidal rotary piston machine with piston follow-up mechanism
US20050276710A1 (en) * 2004-06-15 2005-12-15 Juergen Reiner Piston pump with slot-controlled inlet valve
DE102012010146A1 (de) * 2012-05-24 2013-11-28 Thomas Magnete Gmbh Elektromagnetische Pumpe
US20150144092A1 (en) * 2012-06-21 2015-05-28 Václav Knob Seal assembly for rotary-piston internal-combustin engine
CN109983201A (zh) * 2016-11-22 2019-07-05 伊格尔工业股份有限公司 密封部件

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2314251A1 (de) * 1973-03-22 1974-09-26 Audi Nsu Auto Union Ag Rotationskolben-brennkraftmaschine in trochoidenbauart
JPH0498830U (enrdf_load_stackoverflow) * 1991-02-04 1992-08-26
US20060029503A1 (en) * 2004-08-04 2006-02-09 Norio Takehana Plunger pump and method of controlling discharge of the pump

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US298952A (en) * 1884-05-20 donkin
US1887884A (en) * 1929-07-18 1932-11-15 Powerplus 1927 Ltd Rotary pump machine
US1912845A (en) * 1930-03-17 1933-06-06 Samuel E Dettelbach Rotary pump
US3178103A (en) * 1963-08-16 1965-04-13 Walter H Schnacke Rotary compressor
US3263657A (en) * 1962-12-19 1966-08-02 Daimler Benz Ag Rotary piston engine
US3366317A (en) * 1966-04-30 1968-01-30 Kloeckner Humboldt Deutz Ag Rotary piston internal combustion engine, especially circular piston internal combustion engine
US3410254A (en) * 1965-08-28 1968-11-12 Dornier System Gmbh Inner-axial rotary piston engine with trochoidal piston runner
US3514236A (en) * 1967-03-13 1970-05-26 Vish Machinno Elektrotechnitch Rotary engine with epicyclic rotor
US3583371A (en) * 1969-04-07 1971-06-08 Copeland Refrigeration Corp Pump for rotary machine

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US298952A (en) * 1884-05-20 donkin
US1887884A (en) * 1929-07-18 1932-11-15 Powerplus 1927 Ltd Rotary pump machine
US1912845A (en) * 1930-03-17 1933-06-06 Samuel E Dettelbach Rotary pump
US3263657A (en) * 1962-12-19 1966-08-02 Daimler Benz Ag Rotary piston engine
US3178103A (en) * 1963-08-16 1965-04-13 Walter H Schnacke Rotary compressor
US3410254A (en) * 1965-08-28 1968-11-12 Dornier System Gmbh Inner-axial rotary piston engine with trochoidal piston runner
US3366317A (en) * 1966-04-30 1968-01-30 Kloeckner Humboldt Deutz Ag Rotary piston internal combustion engine, especially circular piston internal combustion engine
US3514236A (en) * 1967-03-13 1970-05-26 Vish Machinno Elektrotechnitch Rotary engine with epicyclic rotor
US3583371A (en) * 1969-04-07 1971-06-08 Copeland Refrigeration Corp Pump for rotary machine

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3994637A (en) * 1974-08-16 1976-11-30 Dornier System Gmbh Rotary piston engine of trochoidal design
US5295814A (en) * 1989-10-04 1994-03-22 Archimedes Associates Inc. Trochoidal rotary piston machine with piston follow-up mechanism
US20050276710A1 (en) * 2004-06-15 2005-12-15 Juergen Reiner Piston pump with slot-controlled inlet valve
US7661936B2 (en) * 2004-06-15 2010-02-16 Robert Bosch Gmbh Piston pump with slot-controlled inlet valve
DE102012010146A1 (de) * 2012-05-24 2013-11-28 Thomas Magnete Gmbh Elektromagnetische Pumpe
DE102012010146B4 (de) * 2012-05-24 2016-07-07 Thomas Magnete Gmbh Elektromagnetische Pumpe
US20150144092A1 (en) * 2012-06-21 2015-05-28 Václav Knob Seal assembly for rotary-piston internal-combustin engine
US9366200B2 (en) * 2012-06-21 2016-06-14 Knob Engines S.R.O. Seal assembly for rotary-piston internal-combustion engine
CN109983201A (zh) * 2016-11-22 2019-07-05 伊格尔工业股份有限公司 密封部件

Also Published As

Publication number Publication date
NL7309596A (enrdf_load_stackoverflow) 1974-02-19
SE380583B (sv) 1975-11-10
GB1419322A (en) 1975-12-31
DE2240100B2 (de) 1976-06-10
IT990125B (it) 1975-06-20
JPS4963812A (enrdf_load_stackoverflow) 1974-06-20
DE2240100A1 (de) 1974-02-28
FR2196666A5 (enrdf_load_stackoverflow) 1974-03-15

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