EP0277114B1 - Machine a refoulement - Google Patents

Machine a refoulement Download PDF

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Publication number
EP0277114B1
EP0277114B1 EP86904164A EP86904164A EP0277114B1 EP 0277114 B1 EP0277114 B1 EP 0277114B1 EP 86904164 A EP86904164 A EP 86904164A EP 86904164 A EP86904164 A EP 86904164A EP 0277114 B1 EP0277114 B1 EP 0277114B1
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EP
European Patent Office
Prior art keywords
displacement
recess
sealing
displacement body
axis
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
EP86904164A
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German (de)
English (en)
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EP0277114A1 (fr
Inventor
Wolfhart Willimczik
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Individual
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Individual
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Filing date
Publication date
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Priority to AT86904164T priority Critical patent/ATE59431T1/de
Publication of EP0277114A1 publication Critical patent/EP0277114A1/fr
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Publication of EP0277114B1 publication Critical patent/EP0277114B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • 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
    • F01C3/00—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members
    • F01C3/06—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees

Definitions

  • the invention relates to a displacement machine with a housing closed by a cover, a displacement body rotating therein and a seal rotating together with the displacement body, the housing comprising an end face facing the displacement body, which includes an angle deviating from 90 ° with the axis of rotation of the displacement body and one to the axis of rotation of the displacement body has a concentric rotation, the displacement body has recesses formed by recesses which run parallel to the axis of rotation of the displacement body and engage sealingly in the recess, the seal, sealing the recess, on the end surface of the housing inclined to the axis of rotation by one against the Axis of rotation of the displacer inclined by a small angle and this intersecting axis rotates and is in positive engagement with the displacer surfaces, such that between the displacements Working spaces are formed in the recess and the seal, the volume of which changes as the displacer body rotates.
  • the displacement body or vane rotor consists of two rigid, one-level vanes that rotate sealingly in the annular groove.
  • the disadvantage here is that only two working chambers can be formed, which results in a relatively high degree of pulsation and other functional disadvantages.
  • the object of this invention is to eliminate these disadvantages without having to accept newly emerging disadvantages.
  • This solution also has the advantage of great freedom of design with regard to the shape, position and number of displacement surfaces, since each recess can now be assigned its own sealing body, so that the sealing body can carry out the slight displacement movements occurring during the course of rotation independently of one another.
  • the displacer body as seen from above — has the outline of a polygon, the sides of which parallel to the axis form the displacement surfaces.
  • the surface producing the recess is a rotating body surface, preferably a cylindrical surface.
  • the axis of the producing rotary body can lie outside, in or within the recess, so that the recess is located on the outer circumference, in the displacer body or on its inner circumference.
  • the displacer body then has an outline similar to a sprocket wheel when viewed from above, in the latter case the corresponding outline on the inner circumference, while the recess or the recesses have the shape of holes in the displacer body when the axis of the producing rotating body lies within the recess .
  • the curved, circular-arc-like shape which the recesses have in the former case and in the latter case allows a greater width of the recess in the housing and thus a larger working volume compared to a flat surface formation of the recesses.
  • the recess has the shape of an annular groove of basically any suitable profile.
  • the boring can also extend as far as a shaft connected in a rotationally fixed manner to the displacer body, so it then has no inner wall formed by the material of the housing.
  • This embodiment can be developed in such a way that the recess is in the form of a spherical shell and that the shaft which is connected to the displacement body in a rotationally fixed manner is pivotably mounted in the housing.
  • the displacement machine has a chamber volume which can be changed during operation and which increases with increasing angle between the drive shaft of the displacement body and the axis around which the sealing bodies rotate.
  • the machine can then be used to convert hydraulic and pneumatic quantities, e.g. use to increase pressure or as a hydraulically driven pump or compressor.
  • the drive shaft of the displacement body can be omitted here.
  • a sealing body is arranged in each recess, which is held in a linear contact with the assigned displacement surfaces and rotates with them.
  • the sealing bodies are circular disks or cylinders which rotate at an incline to the shaft of the rotor and rotate slowly as a result of the different frictional forces acting on their inner and outer circumference. This favors the running-in process between the sliding surfaces involved and prevents the formation of grooves running in the circumferential direction of the displacement body, for example between the top of the sealing body and the inner surface of the cover of the housing.
  • the sealing bodies can be held in contact with the displacement surfaces by a common clamping ring, especially if the recesses are provided on the outer circumference of the displacement body.
  • An improvement is that between the clamping ring and the sealing bodies additional resilient elements are arranged, which individually load the sealing body.
  • the sealing bodies must have hydrostatic relief bores that connect sealed pockets of approximately the same size on opposite large surfaces of the sealing bodies.
  • the individual seals can also be combined and connected to an external shaft.
  • the displacement machine offers the possibility of contactless drive, e.g. by embedding permanent magnets in the area of the outer circumference of the displacement body or by designing it as a short-circuit rotor of an electric motor.
  • the displacement machine proposed here has a very wide range of applications, which can range from pumps and compressors for liquids and gases to compressed air motors, retarders, flow meters, hydrostatic couplings and displacement turbines. Combinations are also possible, not only with each other, but also with other machines, such as a turbomachine in such a way that the displacement body is designed on its outer circumference as an impeller of a centrifugal pump or as a turbine wheel.
  • the displacement machine illustrated in FIGS. 1 to 2b consists of a housing 1 closed by a cover 2, in which a shaft 3 is mounted, which is connected in a rotationally fixed manner to a displacement body 4.
  • the displacer 4 which is additionally shown in the right part of Figure 1 in two side views and a top view, runs in a recess 5 of the housing 1, the shape of which can be imagined as being created by the fact that first a running to the bore of the shaft 3 The cone is turned out concentrically to this hole and then this surface is removed at an angle so that the drawn, the recess 5 containing, inclined end face 6 of the housing 1 is formed.
  • the cover 2 is placed on this end face 6 and screwed to it.
  • the displacer body 4 has the shape of an equilateral triangle in the top view, the side faces of which partially dip into the recess 5 and form the displacer surfaces 4a.
  • a sealing body 7 is assigned to each displacement surface 4a.
  • the sealing bodies 7 run with their lower large surfaces on the end face 6 of the housing 1. Their side surfaces facing the displacer surfaces 4 are chamfered such that there is a line contact along the edge 7a at the end face 6 of the housing between each displacer surface 4a and the associated sealing body 7 1 results.
  • a clamping ring 8 holds the sealing bodies 7, which are approximately circular segment-shaped in plan view, with their straight edges 7a in contact with the respective displacement surfaces of the displacement body 4. In order to keep the tilting moment as small as possible, the clamping ring 8 is arranged on the circumference of the circular segment-shaped sealing bodies 7 as close as possible to their lower large area, where the corresponding counterforce also acts on the sealing edges 7a.
  • An inlet duct 9 opens into the recess 5.
  • the cover 2 contains an outlet duct 10.
  • the recess 5 and the lower large surfaces of the sealing bodies 7 delimit a working space, the cross section of which at the circumferential point 11 is a maximum and at the circumferential point 12 is a minimum (in the example shown is zero).
  • the outlet channel 10 is arranged on the outside of the cover 2 also results in a certain centrifugal pump effect.
  • the sealing bodies 7 revolve around an axis of rotation 13 which, according to FIG. 2a, forms a small angle a with the drive shaft 3 of the displacer 4 (namely the angle by which the end face 6 deviates from a plane perpendicular to the shaft 3), the exactly straight sealing edges 7a of the sealing body 7 in every rotational position in abutment with the relevant exactly flat displacement surface 4a.
  • This embodiment of the displacement machine is suitable because of its high tightness as a pump for small and very small flow rates, is dry-run safe when depressurized and has a high suction capacity.
  • the displacement machine can e.g. can be used as a pump for windscreen washer systems, as a lubricating oil pump or as a vacuum pump.
  • the closing surfaces all adjust themselves.
  • the displacer body 34 is approximately square when viewed from above, that is to say has four displacer surfaces 34a, with which accordingly four sealing bodies 37 in the form of sections in the plan view interact.
  • a cylindrical recess 35 is provided as a housing-side boundary of the working space.
  • the recess 35 can also be viewed as an annular groove concentric with the drive shaft 33 with an inner diameter equal to zero or with a groove base extending up to the shaft 33.
  • the position of the outlet channel 310 in the cover 32 is basically arbitrary.
  • the sealing bodies 37 held by a common, elastic clamping ring 38 in contact with the displacement body 34 act as check valves.
  • the design of the displacement machine has a lower pulsation than the embodiment according to FIGS. 1 to 2b and, moreover, has approximately the same properties as the first embodiment.
  • the recess has the shape of an annular groove 45 with a semicircular arc profile. Both the inlet channel 49 and the outlet channel 410 open into this annular groove 45. At point 412, the volume of the working space or its cross section becomes zero.
  • the displacer body 44 which in turn is triangular in plan, with its displacer surfaces 44a profiled in accordance with the annular groove 45, works together with three sealing bodies 47 which are relieved of hydrostatic stress.
  • the sealing bodies 47 are provided on both large surfaces with a plurality of pockets 47b, preferably of exactly the same surface area, which are connected to one another via bores 47c.
  • sealing bodies 47 form sealing webs 47d which seal the pockets 47b against one another in connection with the end face of the housing 41 or the inner surface of the cover 42.
  • the sealing bodies 47 are held with their sealing edges 47a against the displacement surfaces 44a of the displacement body 44 by means of a clamping ring 48 and an O-ring 481 accommodated in a groove in the sealing bodies 47.
  • the delivery pressure does not exert any forces on the clamping ring 48. Only small axial forces act on the displacer.
  • This type of displacement machine is therefore suitable as a hydraulic pump or hydraulic motor for very high pressures in the range of 1000 bar.
  • FIGS. 5a and 5b Another development of the first embodiment of the displacement machine is shown in FIGS. 5a and 5b.
  • the again triangular displacement body 54 here has, in plan view, arc-shaped displacement surfaces 54a, to which the sealing bodies 57 are adapted, as in the case 4a and 4b have hydrostatic relief bores 57c and the corresponding, sealed pockets 57b on both large surfaces.
  • the circular-arc-like shape of the displacement surfaces enables an enlargement of the working space compared to the embodiment with straight displacement surfaces, the maximum width of which cannot be greater than the difference between the radius of the circle rewritten around the displacement body and the radius of the circle inscribed in the displacement body.
  • the approximately lenticular sealing bodies 57 continue to lie along a sealing line 57a on the displacement surface in question.
  • the inaccuracies caused by the curved sealing line are extremely small and disappear after a short running-in period in which a profile of the displacer surface 54a is formed, in which the sealing line 57a is constantly in contact with the displacer surface over its entire length, if such profiling is not already in production was provided.
  • the sealing bodies 57 are held in contact with the displacement body 54 by an elastic clamping ring 581.
  • FIGS. 6a and 6b once again show the difference between a displacer body 67 which is triangular in the top view with straight displacer surfaces 64a or an arcuate displacer surface 64b in the top view.
  • FIGS. 7a and 7b and 8a and 8b illustrate that the straight or curved design of the displacer surfaces is also possible with a displacer body 74 or 84 which is quadrangular, pentagonal or polygonal in plan view.
  • FIG. 7b additionally shows one of the then lenticular sealing bodies 77, the section of which along the line A-A is shown in FIG. 9a.
  • This sealing body has pockets 77b sealed on both large surfaces, which are connected to one another by a bore 77c for hydrostatic relief. While the sealing on the upper large surface is achieved by webs 77d that have remained standing, sealing strips 77e and 77f are embedded in the edges of the lower large surface, of which the sealing strip 77e simultaneously forms the sealing edge 77a, which on the corresponding sealing surface of the displacer 74 (FIG. 7b ) is present.
  • Figure 9b shows an improvement of this sealing body. While in the case of FIG. 9a the sealing strips 77e and 77f are preferably supported by O-rings for wear compensation, in the further development according to FIG. 9b the sealing strips of the lower large area are also designed as stopping webs, while the sealing body itself consists of two parts 771 and 772, between which a helical compression spring 773 is arranged. An O-ring 774 creates a tight connection between the two parts 771 and 772, but allows the length or thickness change necessary for wear compensation and generated by the spring 773. This enables a very large adjustment range to be achieved. The same axially elastic structure of the sealing body is also possible in all other embodiments.
  • FIG. 9c shows a further embodiment of a sealing body which is elastic in the axial direction and consists of two parts 771 and 772 which are connected to one another via a sleeve-shaped intermediate piece 775 in such a way that the upper part 771 in under the action of a helical compression spring 773 arranged between the two parts is axially displaceable relative to the lower part 772, the sleeve-shaped intermediate piece maintaining the tight connection between the parts 771 and 772.
  • This embodiment of the sealing body is suitable for highly abrasive media. The hydrostatic pressure compensation remains fully intact.
  • the relative displacements of the sealing bodies against each other are extremely small, so that the clamping ring, e.g. 38 in Figures 3a and 3b need only have very little elasticity, i.e. only need not be dimensionally stable and can be made of metal.
  • Figure 10 shows an embodiment in which the actual clamping ring 108 carries additional inner leaf or bow springs 108a, which ensure the pressure of the respective sealing body on the displacement body and thus also compensate for wear.
  • the excellent exemplary embodiment is intended for a four-surface displacement body.
  • FIGS. 11 and 11b show an embodiment of the displacement machine similar to that in FIGS. 1 to 2b, but with a variable delivery volume.
  • the recess 115 must be spherical in shape; the displacement body 114 accordingly has the profile of a spherical cap.
  • the shaft 113 is received in a pivot bearing 50, which is shown only schematically and which can be pivoted in accordance with arrow 51 in accordance with arrow 52.
  • the pivoting movement changes the angle between the shaft 113 and the axis 13 about which the sealing bodies 117 move. This changes the volume of the work area. At an angle of 0 °, the funding is zero.
  • the displacement machine is suitable e.g. as a hydraulic pump with a variable displacement during the run.
  • a clamping ring 118 holds the sealing bodies 117 with their sealing edges 117a in contact with the displacer body 114 via an O-ring 1181.
  • the opening 119 in the recess 115 can e.g. form the inlet duct.
  • Figures 12a and 12b show an embodiment of the displacement machine, which is suitable as a hydraulic motor with very high torque with very little pulsation.
  • the high torque is achieved solely by the fact that the working space is designed in the form of the annular groove 125 with a relatively large diameter, without the swallowing capacity and thus the performance thereby being increased.
  • the low pulsation is based - regardless of this - on the use Formation of a displacer 124 with ten arcuate displacement surfaces 124a with which ten sealing bodies 127 cooperate.
  • the sealing bodies 127 which are designed to be relieved of hydrostatic pressure in the manner already described, have the shape of cylinders and are held in contact with the respective displacement surfaces by a clamping ring 128.
  • the sealing edges 127a is produced by freely rotating the sealing body in its central part. With a suitable choice of material, a slight elasticity of the sealing edge 127a can be achieved; if the displacement surfaces 124a are profiled accordingly, they can also be rigid.
  • the sealing bodies 127 rotate slowly around their axis of symmetry when the displacement machine is in operation. This counteracts scoring (eg as a result of a foreign body between the sealing surfaces). Inlet and outlet channels are very adjacent to you here, corresponding to the distance between successive displacement surfaces 124a. As a hydraulic motor, this displacement machine can also be used for water hydraulics.
  • FIG. 13 A further embodiment of the displacement machine is shown in FIG. 13.
  • the displacement surfaces 134a of the displacement body 134 are also designed in the shape of a circular arc, but point inwards and interact with sealing bodies 137, which are similar to the sealing bodies 127 in FIGS. 12a and 12b.
  • An internal clamping ring 138 holds the sealing body 137 in contact with the displacement surfaces 134a.
  • the displacer body 134 is driven without contact, and is therefore not connected to a drive shaft. Rather, permanent magnets 134b are embedded in its outer circumference, which form one part of a magnetic coupling, the other part, not shown, of which is located outside the housing of the displacement machine, not shown here. This design is therefore suitable as a hermetically sealed pump.
  • the displacer can also be designed as a squirrel-cage rotor of an electric motor and therefore also driven without contact.
  • FIGS. 14a and 14b show an embodiment of a displacement body 145, in which it is designed as a circular disk which has six bores 144 above the annular groove 145 forming the working space, the wall part of each bore lying above and immersing in the annular groove as displacement surface 144a works.
  • a sealing body 157 is seated in each bore, as is shown by way of example in FIG. 15 in section in a pressure-relieved embodiment.
  • This embodiment is also suitable for very high pressures, since only small axial and radial forces act on the displacement body 144.
  • the individual sealing bodies only move slightly against each other at the usually small helix angles of less than 10 °. They can therefore be embedded in a common, elastic ring or, in accordance with FIG. 5b, connected integrally to one another via webs 157c, provided that the sealing bodies 157 consist of a suitable elastic material. This version is particularly suitable for simple, cheap pumps. If the sealing bodies are connected to each other in this way via the displacer body, the axial pressure relief bores can be made so large that both the inlet and outlet channels can be arranged in the cover, so that the pumped medium from the inlet, through the bores and the recess flows to the outlet channel, so that the recess itself does not need to have an inlet or an outlet opening.
  • Figures 16a and 16b illustrate a further embodiment of the displacement machine which is suitable for converting hydraulic or pneumatic quantities and e.g. can be used to increase pressure or as a hydraulically driven pump or compressor.
  • Arranged in the housing 161 are two annular grooves 165a and 165b which are concentric with one another and into which the displacement body 164 engages, each with four displacement surfaces 164a and 164b.
  • the displacer body has no drive shaft. It is only secured against falling out by a ball 170.
  • lenticular displacers 167b are arranged above the outer annular groove 165b of larger cross section and are pressed by an outer clamping ring 168 against the corresponding displacer surfaces 164b. Both ring grooves form separate work spaces with separate inlet and outlet channels (shown somewhat offset in the figures).
  • the outer part of the displacement machine can work as a hydraulic motor and the inner part as a hydraulic pump, the pressure being increased in accordance with the ratio of the volumes of the working spaces.
  • Another possibility is to pressurize the inner annular groove with pressurized water so that the inner part forms the drive of the outer part, which can act as a pump or compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

Une machine à refoulement comprend un logement (1) fermé par un couvercle (2) et contenant un rotor avec des surfaces de refoulement crabotées avec un joint d'étanchéité et tournant avec celui-ci. Les surfaces de refoulement engagent de façon étanche un alésage (5) concentrique à l'axe de rotation (3) du rotor, qui forme l'espace de travail et est agencé dans la surface frontale (6) du logement (1) faisant face au rotor. La surface frontale (6) forme avec l'axe de rotation (3) du rotor un angle différent de 90o. Le rotor est un corps de refoulement (4) qui remplit et recouvre l'alésage (5) et comprend au moins un évidement correspondant à une section le long d'une surface plane ou courbe parallèle à l'axe et formant une intersection avec l'alésage (5). Les parties du corps de refoulement (4) qui pénètrent dans l'alésage (5) forment les surfaces de refoulement (4a). Dans chaque évidement est agencé un corps d'étanchéité (7) posé contre les surfaces de refoulement (4a) le long d'une ligne d'étanchéité. Les corps d'étanchéité (7) forment ensemble le joint d'étanchéité qui tourne avec le rotor.

Claims (8)

1. Machine volumétrique, comprenant un carter (1) fermé par un couvercle (2), un corps de déplacement (4) qui tourne dans ce carter et une garniture (7, 8) qui tourne en même temps que le corps de déplacement,
le carter (1) comprenant, en regard du corps de déplacement (4), une surface frontale (6) qui forme un angle différent de 90° avec l'axe de rotation (3) du corps de déplacement (4) et qui présente une cavité creusée au tour concentrique avec l'axe de rotation (3) du corps de déplacement (4),
le corps de déplacement (4) présentant des faces de déplacement (4a) qui sont formées par des creux, s'étendent parallèlement à l'axe de rotation (3) du corps de déplacement (4) et s'engagent de façon étanche dans la cavité creusée au tour (5),
la garniture (7, 8), qui rend étanche la cavité creusée au tour, tournant, sur la surface frontale (6) du carter (1) inclinée par rapport à l'axe de rotation (3), autour d'un axe qui est incliné d'un petit angle par rapport à l'axe de rotation (3) du corps de déplacement (4) et qui coupe celui-ci, et elle est en prise par emboîtement avec les faces de déplacement (4a), de telle manière qu'il soit formé, entre les faces de déplacement (4a), la cavité creusée au tour (5) et la garniture (7,8), des chambres de travail dont le volume varie avec la rotation du corps de déplacement (4),
caractérisée en ce que la machine volumétrique comprend au moins trois chambres de travail, les faces de déplacement (4a) qui limitent une chambre de travail étant situées dans une surface commune, présentant tout au plus une simple courbure (plan, enveloppe cylindrique, etc.).
2. Machine volumétrique selon la revendication 1, caractérisée en ce que le corps de déplacement (4)-vu de dessus-a le contour d'un polygone dont les côtés parallèles à l'axe constituent les faces de déplacement (4a).
3. Machine volumétrique selon la revendication 1 ou 2, caractérisée en ce que la surface génératrice du creux est une surface de corps de révolution, de préférence une surface d'enveloppe cylindrique.
4. Machine volumétrique selon la revendication 4, caractérisée en ce que l'axe du corps de révolution générateur du creux dans le corps de déplacement est situé en dehors, dans ou en dedans de la cavité creusée au tour (5), de sorte que le creux se trouve à la periphérie extérieure, dans le corps du déplacement ou à la périphérie intérieure de celui-ci.
5. Machine volumétrique selon l'une quelconque des revendications 1 à 4, caractérisée en ce que la cavité creusée au tour (5) atteint un arbre (3) solidaire en rotation du corps de déplacement (4).
6. Machine volumétrique selon la revendication 6, caractérisée en ce que la cavité creusée au tour (115) est en forme de cuvette et en ce que l'arbre (113) solidaire en rotation du corps de déplacement (114) est monté dans le carter (11) de façon à pouvoir osciller (palier oscillant 50).
7. Machine volumétrique selon l'une quelconque des revendications 1 à 6, caractérisée en ce que la section de chambre de travail disponible est partagée entre au moins deux cavités creusées au tour concentriques (165a, 165b).
8. Machine volumétrique selon l'une quelconque des revendications 1 à 7, caractérisée en ce que la garniture est constituée par des corps d'étanchéité qui sont maintenus ensemble par un anneau de serrage (108) et en ce qu'il est disposé en plus, entre l'anneau de serrage (108) et les corps d'étanchéité, des éléments à ressort (108a) qui sollicitent individuellement les corps d'étanchéité.
EP86904164A 1986-07-11 1986-07-11 Machine a refoulement Expired - Lifetime EP0277114B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86904164T ATE59431T1 (de) 1986-07-11 1986-07-11 Verdraengermaschine.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP1986/000411 WO1988000642A1 (fr) 1986-07-11 1986-07-11 Machine a refoulement

Publications (2)

Publication Number Publication Date
EP0277114A1 EP0277114A1 (fr) 1988-08-10
EP0277114B1 true EP0277114B1 (fr) 1990-12-27

Family

ID=8165126

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86904164A Expired - Lifetime EP0277114B1 (fr) 1986-07-11 1986-07-11 Machine a refoulement

Country Status (5)

Country Link
US (1) US4884957A (fr)
EP (1) EP0277114B1 (fr)
JP (1) JPH01500208A (fr)
DE (1) DE3676711D1 (fr)
WO (1) WO1988000642A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3034417B2 (ja) * 1994-02-18 2000-04-17 株式会社東芝 軸流タービンの動翼制振装置
WO2008110155A1 (fr) 2007-03-13 2008-09-18 Cor Pumps + Compressors Ag Pompe ou moteur
JP2009174520A (ja) * 2007-12-26 2009-08-06 Daikin Ind Ltd ゲートロータおよびスクリュー圧縮機
US8379376B2 (en) * 2010-08-18 2013-02-19 General Electric Company Heat management and reduction of high temperatures exposure to components inside energy meter

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2913608C2 (de) * 1979-04-02 1982-10-14 Wolfhart Dipl.-Phys. 8037 Olching Willimczik Drehkolbenartige Rotationskolbenmaschine
DE2946304C2 (de) * 1979-11-16 1983-02-03 Wolfhart Dipl.-Phys. 8037 Olching Willimczik Drehkolbenartige Rotationskolbenmaschine
GB2133473B (en) * 1983-01-10 1987-07-08 George Anthony Fairbairn Rotary positive displacement
DE3308434A1 (de) * 1983-03-10 1984-09-13 Wolfhart Dipl.-Phys. 8037 Olching Willimczik Drehkolbenmaschine
DE3513073A1 (de) * 1985-04-12 1986-11-13 Wolfhart Dipl.-Phys. 8037 Olching Willimczik Starrfluegelverdraengermaschine

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Publication number Publication date
WO1988000642A1 (fr) 1988-01-28
US4884957A (en) 1989-12-05
JPH01500208A (ja) 1989-01-26
EP0277114A1 (fr) 1988-08-10
DE3676711D1 (de) 1991-02-07

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