EP0461494A1 - Entraînement excentrique pour une masse rotative - Google Patents

Entraînement excentrique pour une masse rotative Download PDF

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Publication number
EP0461494A1
EP0461494A1 EP91108941A EP91108941A EP0461494A1 EP 0461494 A1 EP0461494 A1 EP 0461494A1 EP 91108941 A EP91108941 A EP 91108941A EP 91108941 A EP91108941 A EP 91108941A EP 0461494 A1 EP0461494 A1 EP 0461494A1
Authority
EP
European Patent Office
Prior art keywords
receptacle
guide element
eccentric drive
drive according
eccentric
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP91108941A
Other languages
German (de)
English (en)
Other versions
EP0461494B1 (fr
Inventor
Klaus Dieter Dr.-Ing. Emmenthal
Claus Müller
Otto SchÀ¤fer
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.)
Volkswagen AG
Original Assignee
Volkswagen 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 Volkswagen AG filed Critical Volkswagen AG
Publication of EP0461494A1 publication Critical patent/EP0461494A1/fr
Application granted granted Critical
Publication of EP0461494B1 publication Critical patent/EP0461494B1/fr
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
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
    • 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
    • F01C21/008—Driving elements, brakes, couplings, transmissions specially adapted for rotary or oscillating-piston machines or engines

Definitions

  • the invention relates to an eccentric drive for a rotating mass according to the preamble of claim 1.
  • Such turning masses are formed, for example, by the rotors of displacement machines working according to the spiral principle and known from the Motortechnische Zeitschrift, MTZ 46 (1985) 323-327.
  • Such machines are characterized by an almost pulsation-free conveyance of a gaseous working medium, for example consisting of air or an air-fuel mixture, and can therefore also be used with advantage for charging purposes of internal combustion engines.
  • a gaseous working medium for example consisting of air or an air-fuel mixture
  • a number of approximately crescent-shaped working spaces are trapped along the displacement chamber between the spiral-shaped displacement body and the two peripheral walls of the displacement chamber, which work spaces move from the inlet through the displacement chamber to the outlet, their volume constantly reduced and the pressure of the working fluid can be increased accordingly.
  • the cause of the speed is the deflection of the drive shaft or main shaft caused by the inertial forces compared to a minimal deflection of the guide shaft or auxiliary shaft.
  • the resulting deviations in the position of the two eccentric shafts relative to one another can lead to the destruction of the elastic bedding or even one of the bearings.
  • the object of the present invention is to further develop an eccentric drive of the known type and, in particular, to avoid the occurrence of stresses and the associated development of heat.
  • the object is achieved by the characterizing features of patent claim 1.
  • the receptacle for the guide element is essentially elongated in the direction of an imaginary connecting line between the points of attack (compensation direction).
  • the guide element is less rigid in the direction mentioned than in the transverse direction (guide direction) for this purpose, so that the bearing ring can evade in the compensating direction under any pressure that may occur.
  • the receptacle can be designed both as an elongated hole, an oval opening or as an opening with a side open in the compensating direction of the rotating mass. It is crucial that the opening is larger in the direction mentioned than in the guide direction.
  • the guide element and the bearing ring are advantageously adapted to the particular shape of the receptacle. If the guide element is rigid, it can also be moved within the receptacle, for example as a sliding block. Accordingly, the receptacle then has parallel surfaces that permit displacement.
  • An elastic guide element can be non-circular on its outer circumference, corresponding to the shape of the receptacle, as well as circular. A non-circular guide element can be inserted on the one hand in a form-fitting manner and on the other hand with play in the longitudinal direction of the receptacle.
  • An embodiment with an oval receptacle and a corresponding oval elastic guide element, which is arranged in a form-fitting manner in the receptacle, is particularly advantageous.
  • the bearing ring seated inside the guide element is circular. This results in a greater material thickness of the guide element in the compensating direction of the rotating mass than in the circumferential direction. Accordingly, the possibility of yielding to a pressure of the bearing ring is greater in the compensating direction than in the guide direction. Bearing-destroying or heat-generating tensions are effectively avoided in this way.
  • fat pockets can be provided in the guide element and / or in the receptacle for storing a lubricant. This applies in particular to guide elements which can be displaced in the receptacle, both for rigid and for elastic ones.
  • Figures 1 and 2 show the basic structure of a guide device 10 formed by an eccentric arrangement for a displacer 11 of a spiral loader.
  • the latter is eccentrically rotatably arranged in a two-part housing 12, 13 and is guided by a guide shaft 14 with an eccentric pin 15.
  • the guide shaft 14 is itself supported by a ball bearing 16 in the housing part 12.
  • An imaginary connecting line from the guide shaft 14 to a drive shaft, not shown, and back defines a compensation direction.
  • a receptacle 17 for the eccentric pin 15 is formed in the form of a bearing eye.
  • an elastic bed 20 (guide element) in the form of a profile ring is provided between the two in addition to a needle bearing 18 and a bearing ring 19.
  • the needle bearing 18 is sealed off from the outer bearing ring 19 by an additional sleeve 21, so that the grease for the needle bearing 18 cannot emerge from the area of the sleeve 21.
  • the elastic bedding 20 essentially differs in FIGS. 1 and 2.
  • a profile ring with a flat cross section is provided, which is essentially enclosed by the cross sections of the bearing ring 19 and the receptacle 17.
  • the receptacle 17 is secured against axial deflection by a locking ring 22 in the bearing ring 19.
  • an elastic bedding 20 is provided in FIG. 2, which is wider and stronger in cross-section and which in turn axially secures the receptacle 17 by external circumferential beads 23, 24.
  • the elastic bedding 20 with the bearing ring 19 is fixed in FIG connected, e.g. B. by vulcanization or gluing.
  • the opening of the receptacle 17 is not circular, but rather elongated or oval. The exact shape of the opening is described below with reference to the other figures.
  • FIG. 3 shows a simplified representation of the section of the displacer 11 in which the receptacle 17 is provided. This is in the form of an elongated opening, not a circular one.
  • the longer diameter D2 of the receptacle 17 extends approximately in the compensating direction.
  • a displacer 11 corresponds to the rotating mass mentioned at the beginning of the description.
  • the smaller diameter D 1 extends approximately in the circumferential direction of the displacer 11.
  • Figures 4, 5 and 8 show variations in the shape and position of the receptacle 17. According to Figure 4, the longer diameter is inclined with respect to the compensating direction. This is advantageous under certain load conditions in the spiral loader.
  • the receptacle 17 is open in the compensating direction on the outer circumference 25.
  • the guide element can also be rigid, i. H. not be made elastic, for example as a sliding block. The guide element can then slide along the side walls 26, 27 delimiting the receptacle 17 in order to compensate for dimensional or installation tolerances and tension caused by operation.
  • FIG. 8 shows a receptacle 17 with semicircularly curved walls 28, 29, which are connected to one another by straight side walls 30, 31.
  • the curved areas of the receptacle 17 in FIG. 3 are elliptically shaped.
  • FIGS. 6 and 7 show the displacer 11 with elastic bedding 20 inserted into the receptacle 17.
  • the receptacle 17 is elliptically elongated.
  • the shape of the guide element representing the elastic bedding 20 is adapted accordingly and completely fills the receptacle 17.
  • the circular bearing ring 19 is drawn in the guide element.
  • FIG. 7 shows a modification of this.
  • the guide element is circular in shape both inside and outside.
  • a movement of the guide element 20 in the compensating direction (arrow 32) is possible by displacement within the receptacle and / or by an elastic deformation of the material of the elastic bedding.
  • An almost circular design of the contours of the guide element and embedding in an elongated receptacle is furthermore advantageous, but the receptacle is completely filled by the latter by deforming the material of the guide element.
  • Figures 9 to 12 show different variants of the guide element.
  • the guide element consists of an essentially circular base body 33 which has partial beads 34, 35 on opposite regions of its circumference.
  • Figure 10 shows a side view of Figure 9 (or Figure 9 shows a section through Figure 10 along the line IX-IX). Thereafter, three partial beads arranged one above the other are provided on each side.
  • FIG. 11 also shows an almost circular base body 36. However, cross-sectional reinforcements 37, 38 are provided on opposite regions of the circumference, which are connected to the base body 36 to form axially extending spaces 39, 40.
  • FIG. 12 shows a section along the line XII-XII in FIG. 11.
  • FIGS. 13 and 14 show receptacles 17 with guide elements 20 displaceable therein.
  • either the walls of the receptacle 17 have fat pockets 41, 42 or the guide element 20 itself (fat pockets 43, 44).
  • the fat pockets 41 to 44 are preferably not arranged in the compensating direction, but rather transversely thereto. Such fat pockets can also be provided in all other embodiments.
  • Figure 15 shows another special feature.
  • the bearing ring 19 is non-circular, so that there is a positive connection with respect to the guide element 20. This prevents twisting of the two parts against each other. This is of great importance in the proposed elongated shape of the receptacle 17.
  • Another advantageous possibility is to firmly connect the bearing ring 19 to the guide element 20, for. B. by vulcanization or gluing.
  • the guide element 20 can completely fill the receptacle 17 or else have an annular shape or have an elliptical shape and nevertheless not completely fill the receptacle 17.
  • FIG. 16 shows a further variant, this time for a guide element similar to the embodiment according to FIG. 2.
  • the peripheral surface 45 of the guide element 20 is offset from the beads 23, 24 towards the center, so that a gap is formed between the receptacle 17 and the guide element 20. This serves to receive a lubricant, so that the guide element 20 is displaceable in the receptacle 17.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Elimination Of Static Electricity (AREA)
EP91108941A 1990-06-13 1991-05-31 Entraînement excentrique pour une masse rotative Expired - Lifetime EP0461494B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4018887 1990-06-13
DE4018887 1990-06-13

Publications (2)

Publication Number Publication Date
EP0461494A1 true EP0461494A1 (fr) 1991-12-18
EP0461494B1 EP0461494B1 (fr) 1993-07-14

Family

ID=6408318

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91108941A Expired - Lifetime EP0461494B1 (fr) 1990-06-13 1991-05-31 Entraînement excentrique pour une masse rotative

Country Status (3)

Country Link
EP (1) EP0461494B1 (fr)
DE (1) DE59100184D1 (fr)
ES (1) ES2042325T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7789640B2 (en) * 2004-12-21 2010-09-07 Daikin Industries, Ltd. Scroll fluid machine with a pin shaft and groove for restricting rotation

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2532011A1 (fr) * 1982-08-20 1984-02-24 Volkswagen Ag Machine refoulante pour fluides compressibles
DE3338737A1 (de) * 1982-10-27 1984-05-03 Hitachi, Ltd., Tokio/Tokyo Stroemungsmaschine in spiralbauweise

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2532011A1 (fr) * 1982-08-20 1984-02-24 Volkswagen Ag Machine refoulante pour fluides compressibles
DE3338737A1 (de) * 1982-10-27 1984-05-03 Hitachi, Ltd., Tokio/Tokyo Stroemungsmaschine in spiralbauweise

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7789640B2 (en) * 2004-12-21 2010-09-07 Daikin Industries, Ltd. Scroll fluid machine with a pin shaft and groove for restricting rotation
US8246331B2 (en) 2004-12-21 2012-08-21 Daikin Industries, Ltd. Scroll fluid machine with a pin shaft and groove for restricting rotation
EP2628955A1 (fr) * 2004-12-21 2013-08-21 Daikin Industries, Ltd. Machine de défilement de fluide

Also Published As

Publication number Publication date
EP0461494B1 (fr) 1993-07-14
DE59100184D1 (de) 1993-08-19
ES2042325T3 (es) 1993-12-01

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