EP0290864B1 - Innenachsige Drehkolbenmaschine - Google Patents

Innenachsige Drehkolbenmaschine Download PDF

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Publication number
EP0290864B1
EP0290864B1 EP88106729A EP88106729A EP0290864B1 EP 0290864 B1 EP0290864 B1 EP 0290864B1 EP 88106729 A EP88106729 A EP 88106729A EP 88106729 A EP88106729 A EP 88106729A EP 0290864 B1 EP0290864 B1 EP 0290864B1
Authority
EP
European Patent Office
Prior art keywords
housing
rotary piston
outer rotor
valve body
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
EP88106729A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0290864A2 (de
EP0290864A3 (en
Inventor
Arno Förster
Gerhard Oberholz
Christiane Römuss
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.)
Howden Turbo GmbH
Original Assignee
Siemens Turbomachinery Equipment GmbH
Kuehnle Kopp and Kausch AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Siemens Turbomachinery Equipment GmbH, Kuehnle Kopp and Kausch AG filed Critical Siemens Turbomachinery Equipment GmbH
Priority to AT88106729T priority Critical patent/ATE68557T1/de
Publication of EP0290864A2 publication Critical patent/EP0290864A2/de
Publication of EP0290864A3 publication Critical patent/EP0290864A3/de
Application granted granted Critical
Publication of EP0290864B1 publication Critical patent/EP0290864B1/de
Anticipated expiration legal-status Critical
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
    • 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
    • F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F01C1/103—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • 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
    • F01C20/24—Control of, monitoring of, or safety arrangements for, machines or engines characterised by using valves for controlling pressure or flow rate, e.g. discharge valves
    • F01C20/26—Control of, monitoring of, or safety arrangements for, machines or engines characterised by using valves for controlling pressure or flow rate, e.g. discharge valves using bypass channels

Definitions

  • the invention relates to a rotary piston machine according to the features specified in the preamble of patent claim 1.
  • the inner rotor is mounted eccentrically to the axis of rotation of the outer rotor and has three engagement parts which can engage in four recesses in the outer rotor in accordance with the current rotational position.
  • a high level of manufacturing effort is necessary and compression could previously only be achieved if the medium to be conveyed was itself suitable as a sealant.
  • an inner-axis rotary piston machine is known, the inner rotor of which has two engagement parts and the outer rotor of which has three recesses.
  • the inner surfaces, which delimit the recesses of the outer rotor, are designed as flat surfaces in order to enable simple manufacture.
  • the inner rotor In order to enable a rolling motion of the inner rotor on the aforementioned flat surfaces of the outer rotor, the inner rotor must have a special geometry, the production of which nevertheless requires a not inconsiderable effort.
  • the formation and arrangement of the bearings is particularly problematic of inner rotor and outer rotor. Very tight manufacturing tolerances have to be observed so that on the one hand excessive surface pressures are avoided and on the other hand no undesirably large gaps can occur between the inner rotor and outer rotor.
  • the invention has for its object to further develop the internal-axis rotary lobe machine of the type mentioned in such a way that a high level of functional reliability and a long service life can be achieved with a simple construction taking into account permissible manufacturing tolerances.
  • the proposed rotary lobe machine is characterized by an expedient construction and has a high level of functional reliability and a long service life.
  • the number of components to be coordinated with respect to the manufacturing tolerances is small and the manufacturing effort is limited.
  • Due to the one-piece molding of the base on the housing the bearings of the inner rotor and of the outer rotor are expediently integrated into the housing, as a result of which an exact geometric allocation of the inner rotor is both is guaranteed with respect to the outer rotor as well as with respect to the housing.
  • the bearing of the inner rotor is arranged on the extension which extends into the drive disk and can therefore be designed with a comparatively small diameter.
  • the machining surfaces and corresponding manufacturing tolerances that are required in the case of a multi-part construction of the housing and the bottom are eliminated. With little work and assembly effort, high accuracy is reliably ensured even when manufacturing in large quantities.
  • the arrangement of the gearbox in the housing cover, which closes the housing, enables a compact design with a few components to be coordinated in terms of their tolerances.
  • the gearbox is arranged in the housing cover, which closes the cup-shaped housing.
  • a line opening into the gear chamber which can be arranged externally outside the housing or can be integrated as a longitudinal bore in the housing, can expediently equalize the pressure to the suction nozzle and prevent lubricant from being pressed into the working spaces.
  • the gear is easily accessible for maintenance without having to remove the rotors.
  • the pinion of the gearbox expediently connected to the shaft of the inner rotor remains accessible in the assembled state of the rotors.
  • the housing cover or even rotor bearings do not have to be removed in order to change the rotational position of the pinion with respect to the inner rotor for the exact setting of the tooth flank play.
  • the pinion can easily be turned on the shaft to obtain the required angle of rotation setting.
  • the shaft can also be led out through the end cover, for example to couple an alternator or another unit to the shaft of the inner rotor.
  • a centrifugal plate is arranged in the gearbox on the inner rotor and / or on the outer rotor.
  • the lubricant is conveyed to the ring gear of the outer rotor or to the pinion.
  • a recirculation valve is arranged between the pressure port and the suction port, which, in certain operating states, enables regulation by returning the air from the pressure port to the suction port.
  • This valve can be used for boost pressure control and can also be advantageously used in combination for partial load control.
  • a valve of this type solves the task of reducing consumption in the part-load range by means of part-load control and, on the other hand, limiting the boost pressure in the full-load range by boost pressure control.
  • This valve is expediently provided in the above-described rotary piston machine according to the US Pat. No. 4,714,417 explained at the outset.
  • the suitably combined valve can also be provided for charging in other engines, in particular in automotive engines.
  • the air mass flow conveyed by the machine is fed wholly or in part to the suction side as required, the two valve components being expediently housed in a common housing.
  • the valve intended for partial load control When the engine to be charged with the rotary lobe engine is idling, the valve intended for partial load control is open and the engine is operating in suction mode. As the load increases, the partial load valve expediently closes continuously in a predeterminable range and the motor is charged in the required manner by means of the rotary piston machine. In the full load range, the valve provided for the boost pressure control opens when an adjustable maximum boost pressure is reached. When the load is reduced, these processes take place in reverse order.
  • the air recirculation valve is arranged in a cover which is tightly connected to the housing and advantageously has the valve guide and the return line. The proposed valve requires a small amount of space and weight, which is particularly important in motor vehicle engines.
  • Figure 1 shows an axial longitudinal section of the inner-axis rotary lobe machine with a cup-shaped housing 2, which has a bottom 4 and is closed at the other axial end with a single housing cover 6.
  • An inner rotor 8 is arranged in the interior of the housing 2 and is rotatably mounted about an axis 10 by means of a shaft 12 which is led out through the base 4.
  • a bearing 16 is arranged in a shoulder 14 of the base 4, which bearing is expediently designed as a combined axial / radial bearing.
  • a second bearing 18 is arranged in the housing cover 6, which is preferably designed as a needle bearing.
  • the bearing 16 provided in the projection 14 is surrounded by a pot-shaped pulley 20 which lies essentially in the same radial plane as the bearing 16 mentioned and is connected to the shaft 12 in a rotationally fixed manner.
  • the inner rotor 8 can be made of plastic or light metal and is connected directly to the shaft 12, in particular by composite casting. This one-piece construction ensures a not inconsiderable simplification of assembly.
  • the bearing 16 and the pulley 20 are fixed on the shaft 12 by means of a nut 22 screwed onto a thread at the shaft end, the support on the inner rotor 8 being carried out by means of a spacer sleeve 24.
  • an outer rotor 26 is arranged in the interior of the housing 2, work spaces being formed in a known manner with the inner rotor 8.
  • the relevant principles and the mode of operation result from the aforementioned US Pat. No. 4,714,417, to which reference is expressly made here.
  • the bottom 4 of the housing 2 has a ring 28 extending axially into the end of the outer rotor 26, on the outer surfaces of which the bearing 30 of the outer rotor 26 is arranged.
  • the outer rotor 26 has three engagement parts 34 distributed over the circumference, which are in one piece are formed with a rotor disk 36. Also important is the axially spaced arrangement of the bearing 30 in the ring 28 with respect to the bearing 16 from the inner rotor 8, so that the bearing 30 of the outer rotor 26 has a comparatively small diameter.
  • the outer rotor 26 has a ring 38 which is connected to the engaging parts 34 by means of screws 40.
  • the second bearing 32 for the outer rotor 26 is arranged according to the invention within the rotor ring 38 on the housing cover 6.
  • an internally toothed wheel 42 is expediently connected to the outer rotor 26.
  • the internally toothed wheel 42 meshes with a pinion 44 which is arranged on the shaft 12 of the inner rotor 8 in a frictionally engaged manner.
  • the pinion 44 is braced against a shaft collar 50 by means of a nut 46 via a bearing sleeve 48.
  • the backlash of the gear and the angular position of the inner rotor 8 and outer rotor 26 can be adjusted without difficulty due to this special arrangement.
  • the gear chamber 52 is closed off by means of an end cover 54 fastened in an opening 53 in the housing cover 6. By removing the end cover, the gear chamber 52 is easily accessible at any time in order to carry out maintenance or adjustment measures. It is important here that due to the proposed integration and arrangement of the transmission and the design of the housing cover 6 and end cover 54, good accessibility and ease of service with a simple construction is achieved.
  • centrifugal plate 56 connected to the inner rotor 8 and a centrifugal plate 58 connected to the outer rotor 26, by means of which the lubricant supply is reliably ensured. Additional fasteners are not necessary insofar as the centrifugal plate 56 is fixed on the inner rotor 8 or the outer rotor 26 by means of the nut 46 already mentioned and the centrifugal plate 58 is fixed by means of the screws 40.
  • a line 60 opens into the gear chamber 52 and leads into the intake port is guided and serves to equalize the pressure. In this way, pressure build-up is expediently prevented in the gear chamber 52, as a result of which lubricant could otherwise be pressed into the work spaces.
  • the shaft 12 is passed through the end cover 54, the gear chamber 52 being sealed by means of a shaft seal.
  • Another unit for example the alternator of a motor vehicle, can be connected to the shaft journal protruding beyond the end cover 54.
  • the outer rotor 26 has a piston ring 68 at each of its two ends, which bear against the cylindrical inner surface 70 of the housing 2. It is also essential that, as seen from the working spaces or the inner rotor 8, an annular groove 72 is arranged in each case in front of the piston rings 68 in the outer surface of the outer rotor 26. A non-uniform loading of the piston ring 68 is avoided by these two ring grooves 72. In this respect, the narrow annular gap between the outer rotor 26 and the inner surface 70 of the housing, which exists axially between the working spaces and the annular groove, is also important in order to avoid an impermissible pressure loss between the working spaces.
  • FIG. 2 shows a radial section along section line II according to FIG. 1, the suction nozzle 62 with the inlet opening 63 and the pressure nozzle 65 with the outlet opening 64 now being recognizable.
  • the above-described line 60 opens into the suction port 62.
  • the line 60 shown here externally outside the housing 2 can also be integrated directly into the housing 2 in the context of this invention and, for example, be formed by a bore in a correspondingly thickened wall of the housing is arranged.
  • the inner rotor 8 is connected directly to the shaft 12. This can be achieved in particular by composite casting, the inner rotor 8 being cast around the shaft 12 previously produced. This one-piece construction of inner rotor 8 and shaft 12 leads to a not inconsiderable simplification of assembly.
  • the three segments or engaging parts 34 and the three work spaces 66 are clearly visible here.
  • the rotor and engaging parts 34 are connected on the drive side to the rotor disk explained above in one piece.
  • the recesses located between the segments, which define the work spaces, are created by machining in one piece, which ensures exact dimensional accuracy.
  • the engagement parts 9 of the inner rotor 8 and also the segments of the outer rotor 26 are expediently designed as hollow bodies in order to reduce the mass.
  • FIG. 3 shows an enlarged view of the inner rotor 8, which has a profiling or longitudinal grooves 74 running in the axial direction on its surface.
  • the tips of this profiling projecting above the surface are removed or bent. An optimal seal between the inner rotor 8 and the outer rotor and consequently the working spaces is ensured.
  • FIG. 4 shows a section through an embodiment of the rotary piston machine in accordance with the section line IV, the suction port 62 and the pressure port 65 being cut and the housing 2 being partially visible in a top view.
  • a valve 76 and a return line 78 are provided between the pressure port 65 and the suction port 62 in order to enable a return from the pressure port to the suction port in certain operating states.
  • a valve body 82 is guided in a valve cover 80 and is pressed by means of a spring 84 onto the valve seat 86 which is advantageously provided on the housing 2.
  • the valve 76 is expediently integrated into this valve cover 80, which is firmly connected to the housing 2 via a seal 88.
  • the valve cover 80 also contains the return line 78, through which air can flow back into the suction port 62 if the pressure in the pressure port 65 is too high.
  • FIG. 5 shows a section through a special embodiment of the valve 76.
  • This valve is not only for the boost pressure limitation in the full-load range, as in the embodiment according to FIG. 4 but also trained for partial load control.
  • the valve housing 90 contains a pressure channel 92 and a suction channel 94, between which the return line 78 is present.
  • the pressure channel 92 leads to the pressure port 65 and the suction channel 94 leads to the suction port 62 of the housing 2 of the rotary piston machine explained above.
  • the housing 90 can be connected to the housing of the rotary lobe machine in accordance with the valve cover explained with reference to FIG. 4.
  • the valve contains the first valve body 82, which is provided for boost pressure control.
  • This first valve body 82 is arranged in a second valve body 96 so as to be displaceable in the direction of arrow 98.
  • the second valve body 96 is used for partial load control and is likewise arranged in the housing 90 so as to be displaceable in the direction of the arrow 98.
  • the first valve body 82 is supported by means of the spring 84, a plate 100 and an adjusting screw 102 and a cover 104 which is screwed to the second valve body 96.
  • the spring preload of the spring 84 is changed and thus the maximum boost pressure at which the valve body 82 can be moved against the spring force in the full-load range is set.
  • the second valve body 96 contains an inlet opening 106 and one or more lateral outlet openings 108. According to the invention, with the valve combined in this way, the inlet opening 106 can be blocked off with respect to the outlet opening 108 in accordance with the position of the first valve body 82 shown.
  • the second valve body 96 is shown in the position which it assumes when the engine to be charged is idling. Pressure channel 92 and suction channel 94 are connected to one another via the partial load opening 114 and the engine can operate in suction mode.
  • the partial load valve or the valve body 96 can be controlled according to the invention depending on the position of the accelerator pedal of the engine. As will be explained below, the partial load valve can be actuated mechanically, for example by means of a cable pull. Furthermore, the control can also be done pneumatically via the boost pressure, hydraulically or electrically.
  • a shaft 110 is provided, which is rotatably mounted about an axis perpendicular to the drawing plane in a manner not shown here.
  • a cable is guided on this shaft, which is connected directly to the accelerator cable or accelerator pedal for controlling the engine.
  • the partial load valve 96 is expediently controlled in such a way that the valve body 96 is not adjusted for an accelerator pedal travel in the range from 0 to 2/3.
  • the partial load opening 114 present between the valve seat 112 and the second valve body 96 is, as shown, opened in the area mentioned and the engine operates in suction mode.
  • the partial load opening 114 is expediently closed continuously.
  • the connection between the pressure channel 92 and the suction channel 94 is closed by means of the second valve body 96. If the boost pressure present in the pressure channel 92 then exceeds the maximum boost pressure set via the boost pressure spring 84 by means of the adjusting screw 102, the first valve body 82 is moved against the biasing force of the spring 84. The air can now flow from the pressure channel 92 through the inlet opening 106 to the outlet openings 108 and via the return line 78 into the suction channel 94.
  • the combination of partial load control and boost pressure control with valve 76 ensures on the one hand a reduction in consumption in the partial load range and an effective boost pressure limitation in the full load range of the engine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)
  • Centrifugal Separators (AREA)
  • Crushing And Pulverization Processes (AREA)
  • Compressor (AREA)
EP88106729A 1987-05-14 1988-04-27 Innenachsige Drehkolbenmaschine Expired - Lifetime EP0290864B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88106729T ATE68557T1 (de) 1987-05-14 1988-04-27 Innenachsige drehkolbenmaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3716083 1987-05-14
DE19873716083 DE3716083A1 (de) 1987-05-14 1987-05-14 Innenachsige drehkolbenmaschine

Publications (3)

Publication Number Publication Date
EP0290864A2 EP0290864A2 (de) 1988-11-17
EP0290864A3 EP0290864A3 (en) 1989-07-12
EP0290864B1 true EP0290864B1 (de) 1991-10-16

Family

ID=6327508

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88106729A Expired - Lifetime EP0290864B1 (de) 1987-05-14 1988-04-27 Innenachsige Drehkolbenmaschine

Country Status (9)

Country Link
US (1) US4943213A (cs)
EP (1) EP0290864B1 (cs)
JP (1) JPS64303A (cs)
CN (1) CN1010793B (cs)
AT (1) ATE68557T1 (cs)
BR (1) BR8802326A (cs)
CS (1) CS324988A3 (cs)
DE (2) DE3716083A1 (cs)
YU (1) YU92188A (cs)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4670178A (en) * 1985-09-09 1987-06-02 Allergan Pharmaceuticals, Inc. Method for the simultaneous cleaning and disinfecting of contact lenses
DE3911541C1 (cs) * 1989-04-08 1990-03-29 Aktiengesellschaft Kuehnle, Kopp & Kausch, 6710 Frankenthal, De
DE3911540C1 (cs) * 1989-04-08 1990-03-29 Aktiengesellschaft Kuehnle, Kopp & Kausch, 6710 Frankenthal, De
CH685450A5 (de) * 1992-04-01 1995-07-14 Lindau Tech Forsch & Entw Gmbh Innenachsige Drehkolbenmaschine.
DE19800002A1 (de) * 1998-01-02 1999-07-08 Linde Ag Hydrostatisches Aggregat zum Antrieb einer Arbeitsmaschine
JP2003269329A (ja) * 2002-03-15 2003-09-25 Sanden Corp 自動車用コンプレッサ
ITTV20030089A1 (it) * 2003-06-19 2003-09-17 Orlando Canal Meccanismo per gas-dinamica azione volumetrica alterno rotativa a 60 grado, "gavara-60", per uso generale e particolarmente per motori endotermic
JP5969226B2 (ja) * 2012-03-14 2016-08-17 サンデンホールディングス株式会社 流体機械
SK6803Y1 (sk) 2013-01-06 2014-06-03 Kujovic Jozef Pracovný priestor s rotačne sa pohybujúcim piestom
CN105108485A (zh) * 2015-09-08 2015-12-02 连云港市天意消防器材有限公司 灭火器导管组装机

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0178392A1 (de) * 1984-08-21 1986-04-23 Robert Bosch Gmbh Zahnradmaschine
WO1987001760A1 (en) * 1985-09-23 1987-03-26 Sundstrand Corporation Hydraulic displacement unit and method of assembly thereof

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Publication number Priority date Publication date Assignee Title
DE547826C (de) * 1928-07-27 1932-04-07 Expl Des Procedes Maurice Lebl Zahnradverdichter
US1955799A (en) * 1931-08-24 1934-04-24 Gen Motors Corp Pressure control system for blower-fed two-cycle engines
US2177976A (en) * 1935-08-19 1939-10-31 Brauer Walter Motor
US3139835A (en) * 1962-08-15 1964-07-07 Davey Compressor Co Rotary pump or motor
US4017221A (en) * 1976-02-27 1977-04-12 Caterpillar Tractor Co. Combined unloading and relief valve for pump unloading circuit
DE2844019A1 (de) * 1978-10-09 1980-04-17 Leybold Heraeus Gmbh & Co Kg Vakuumpumpe, insbesondere waelzkolben-vakuumpumpe
US4466414A (en) * 1981-07-07 1984-08-21 Nippondenso Co., Ltd. Supercharged internal combustion engine
EP0083491A1 (en) * 1981-12-24 1983-07-13 Concentric Pumps Limited Gerotor pumps
US4502283A (en) * 1982-09-24 1985-03-05 General Motors Corporation Turbocharged engine driven positive displacement blower having a bypass passage
US4722672A (en) * 1983-02-17 1988-02-02 Rinneer Arthur E Hydraulic energy-conversion device
JPS59213984A (ja) * 1983-05-20 1984-12-03 Nippon Piston Ring Co Ltd ベ−ン形回転圧縮機の軸受装置
CH664423A5 (de) * 1984-06-12 1988-02-29 Wankel Felix Innenachsige drehkolbenmaschine.
JPS61223290A (ja) * 1985-03-27 1986-10-03 Honda Motor Co Ltd ベ−ンポンプに於けるロ−タシ−ル構造
WO1986006797A2 (en) * 1985-05-09 1986-11-20 Barmag Aktiengesellschaft Variable capacity pump
US4740140A (en) * 1985-12-11 1988-04-26 Sundstrand Corporation Pump having integral switch and bypass valve

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0178392A1 (de) * 1984-08-21 1986-04-23 Robert Bosch Gmbh Zahnradmaschine
WO1987001760A1 (en) * 1985-09-23 1987-03-26 Sundstrand Corporation Hydraulic displacement unit and method of assembly thereof

Also Published As

Publication number Publication date
YU92188A (en) 1990-12-31
US4943213A (en) 1990-07-24
CS324988A3 (en) 1992-08-12
JPS64303A (en) 1989-01-05
CN1010793B (zh) 1990-12-12
CN1030961A (zh) 1989-02-08
EP0290864A2 (de) 1988-11-17
BR8802326A (pt) 1988-12-13
DE3865516D1 (de) 1991-11-21
DE3716083A1 (de) 1988-11-24
EP0290864A3 (en) 1989-07-12
ATE68557T1 (de) 1991-11-15

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