EP0729554A1 - Moteur a piston alternatif - Google Patents

Moteur a piston alternatif

Info

Publication number
EP0729554A1
EP0729554A1 EP94913589A EP94913589A EP0729554A1 EP 0729554 A1 EP0729554 A1 EP 0729554A1 EP 94913589 A EP94913589 A EP 94913589A EP 94913589 A EP94913589 A EP 94913589A EP 0729554 A1 EP0729554 A1 EP 0729554A1
Authority
EP
European Patent Office
Prior art keywords
segments
sealing
segment
cylinder wall
reciprocating piston
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.)
Withdrawn
Application number
EP94913589A
Other languages
German (de)
English (en)
Inventor
Hans Helpap
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.)
KKM KREIS-KOLBEN-MOTOREN GmbH
Original Assignee
KKM KREIS KOLBEN MOTOREN GmbH
KKM KREIS-KOLBEN-MOTOREN GmbH
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 KKM KREIS KOLBEN MOTOREN GmbH, KKM KREIS-KOLBEN-MOTOREN GmbH filed Critical KKM KREIS KOLBEN MOTOREN GmbH
Publication of EP0729554A1 publication Critical patent/EP0729554A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/06—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction using separate springs or elastic elements expanding the rings; Springs therefor ; Expansion by wedging
    • F16J9/061—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction using separate springs or elastic elements expanding the rings; Springs therefor ; Expansion by wedging using metallic coiled or blade springs
    • F16J9/063—Strip or wire along the entire circumference

Definitions

  • the present invention relates to a reciprocating piston machine, in particular a reciprocating piston engine or compressor, with at least one working space delimited by a cylinder wall and at least one piston oscillating within the cylinder wall, the piston having at least one circumferential groove in which a seal sealing the piston against the cylinder wall is received.
  • Piston engines of this type are generally known.
  • a plurality of piston rings are used to seal the piston against the cylinder wall.
  • the piston rings are designed as slotted spring rings, primarily made of metal (special cast iron, bronze or steel).
  • the piston rings are arranged in the upper part of the piston.
  • ring flutter A problem which occurs in known reciprocating piston engines, the pistons of which are equipped with the piston rings described above, is the so-called “ring flutter", which is particularly common in high-speed, high-performance engines, e.g. B. racing engines, occurs and is due to resonance effects. Periodic gas and mass forces cause the piston ring to vibrate when the excitation frequency and the natural vibration frequency of the piston ring coincide. In the "ring flutter” caused by this, the gas passage from the work space to the crankcase increases sharply. In addition to the normal leakage, which is unavoidable due to the slotted piston ring design, there are additional working pressure losses which sometimes have a noticeable performance-reducing effect. In addition, "ring flutter" is one of the causes that lead to ring breaks.
  • the present invention has for its object to provide a reciprocating piston machine which does not have the disadvantages described above.
  • the aim is to create a reciprocating piston machine in which the seal inserted into the circumferential groove of the piston reliably seals the piston against the cylinder wall at all speeds, at the same time reducing the risk of damage to the seal and increasing its service life should.
  • the seal comprises at least two segment rings having a plurality of sealing segments and lock segments and at least one spring element, the sealing segments and the lock segments tapering radially inwards and outwards in the opposite direction and inside each segment ring are provided alternately and wherein the sealing segments of the at least two segment rings alternately overlap each other and are biased radially outward into contact with the cylinder wall by means of the at least one spring element, and that an anti-rotation device acting between the at least two segment rings is provided.
  • the seal for sealing the piston against the cylinder wall is thus made up of at least two axially abutting segment rings.
  • Each of these segment rings consists of a plurality of sealing segments, which preferably taper radially inwards, and just as many lock segments, which preferably taper radially outwards. Sealing segments and lock segments alternate within each segment ring and lie against one another. The sealing segments extend over a larger arc area than the lock segments, so that in each case one sealing segment of a segment ring overlaps two sealing segments of the adjacent segment ring at the end in order to form a continuous sealing boundary.
  • the anti-rotation device that acts between the at least two segment rings ensures that a sealing segment of one segment ring always overlaps two sealing segments of the other segment ring at the end, even if the package consisting of the at least two segment rings is located overall in the groove of the piston can twist.
  • the sealing elements are preloaded r-adial outwards in contact with the cylinder wall; for this purpose, the spring element can either act directly on the sealing segments, or else it acts on the lock segments, which in turn prestress the sealing segments in contact with the cylinder wall.
  • each segment ring By dividing each segment ring into a plurality of sealing segments and lock segments, the mass of each individual vibratable structure is reduced to such an extent that the natural vibration frequency rises to a value which is well above the vibrations caused by gas and / or mass forces, even of high-speed ones High-performance reciprocating machines.
  • the seal provided according to the invention can therefore not resonate even in the case of high-performance motors. In this way, a "ring flutter" is reliably avoided and the seal is always sealing against the cylinder wall. There is also no fear of a breakage caused by the seal vibrating naturally. This also contributes to the fact that the segment rings built up from lock segments and sealing segments are self-contained. This also applies to advanced wear of the seal at the sealing boundary with the cylinder and.
  • Sealing strips for a rotary piston internal combustion engine are known from WO90 / 01676, with which the rotating pistons are sealed off from the housing and the two piston carriers.
  • a separate sealing strip is provided, which is composed of several wedge-shaped segments.
  • the sealing strips known from this publication cannot be used in reciprocating piston machines with a curved, self-contained sealing limit.
  • this document contains no suggestions for solving the problem described at the outset ("ring flutter") of conventional reciprocating piston machines.
  • the present invention can preferably be used wherever a very good supply of lubricant to the contact surfaces of the seal on the cylinder surface is required.
  • the seal provided in machines according to the invention has good wear behavior and thus a long service life.
  • a further particular advantage is that asymmetrical piston grinding is not required in the machines according to the invention.
  • the sealing effect of the seal used in the context of the invention is so good that it is particularly suitable for increasing the performance of conventional machines - even when overhauling them.
  • conventional machines usually have several piston rings, only one seal is required in machines according to the invention in order to achieve an equivalent sealing effect.
  • the sealing segments of each segment ring provided within the scope of the invention preferably do not abut one another.
  • the lock segments preferably do not rest on the cylinder wall.
  • the sealing segments of a segment ring do not abut against each other on the cylinder wall and the lock segments inserted between two sealing segments do not abut the cylinder wall, there is between each two sealing segments and the lock segment of a segment ring arranged between them and the cylinder wall formed a channel through which lubricant can directly reach the surface of the sealing segment of the second segment ring arranged behind the cylinder wall.
  • such a design of the seal enables effective wear compensation in a particularly simple manner.
  • At least one segment ring is provided with circumferentially extending lubricant grooves into which lubricant channels open which face the lock segments of the other segment ring.
  • Lubricant can thus reach the lubricant channels of the other segment ring through channels which are formed between the cylinder wall and two sealing segments and the lock segment of a segment ring arranged between them, and via the lubricant grooves via the surfaces of the sealing segment which abut the cylinder wall ⁇ elements of the second segment ring are distributed.
  • the lubricant grooves can also be used to control the force with which the sealing segments bear against the cylinder wall. be set when they are pressurized. This is because the contact pressure of the sealing segments against the cylinder wall, which is generated by the pressure acting on the opposite surface (“rear side”) of the sealing segments, is reduced by the proportion of the area of the lubricant grooves in the total area of the sealing segments lying against the cylinder wall. If the invention is to be used in machines operating at the highest pressures, the contact pressure of the sealing segments against the cylinder wall can be adjusted by suitable dimensioning of the lubricant grooves in such a way that it does not exceed a certain value.
  • the wedge direction of the lock segments is directed radially outwards onto the cylinder wall and that of the sealing segments is directed radially inwards.
  • a reverse wedge direction can prove to be useful, especially if, by suitable choice of the wedge angle and appropriate design and dimensioning of the surfaces of the sealing segments and the lock segments exposed to pressure, a reduction in the contact pressure with which the sealing segments operate against the cylinder wall during operation be pressed, should be achieved.
  • the anti-rotation lock acting between the at least two segment rings can additionally change the position of the seal in the groove receiving this in a preferred further development of the invention establish.
  • an adjustment element can be provided, in particular, which in an overlap area between the sealing segments of the at least two segment rings is arranged.
  • an adjustment element in particular an adjustment pin comes into consideration, which is inserted into a bore in each of a sealing segment of the at least two segment rings.
  • a spring element common to a plurality of segment rings can also serve, with a suitable design, as a safeguard against rotation of the segment rings against one another.
  • the at least one spring element with which the sealing segments are prestressed in the radial direction in abutment against the cylinder wall can act directly on the sealing segments. In a preferred development of the invention, however, it acts on the lock segments which, due to their wedge shape, spread the sealing segments evenly in the circumferential direction and preload them radially in contact with the cylinder wall.
  • At least one axially acting spring element is expediently provided, which prestresses the at least two segment rings to bear against one another. This prevents an axial gap from forming between the two segment rings, which could adversely affect the effect of the seal.
  • Such an axially acting spring element can also compensate for manufacturing tolerances of the groove receiving the seal. It is particularly expedient if at least one plate spring is provided as the axially acting spring element, which is supported on an axially adjustable counter-holder. Due to the axial adjustability of the counter-holder, the force with which the two segment rings are prestressed against one another can be set to an optimal value.
  • An essential advantage of the invention lies in the fact that the sealing effect remains good even when the sealing segments are worn due to an optimal readjustment of the elements exposed to the wear.
  • the force with which the sealing segments are prestressed against the cylinder wall by the spring element can be adjusted.
  • a pressure ring which consists of as many pressure segments as lock segments are provided, and an axially displaceable wedge ring which has as many wedge surfaces acting on the pressure segments, can be provided.
  • the pressure segments act in the radial direction on the lock segments. By axially moving the wedge ring, the pressure segments are pressed more or less strongly in the radial direction against the lock segments due to the inclination of the wedge surfaces.
  • the wedge ring can also act as an anti-rotation device for the two segment rings; because turning the pressure segments with respect to the wedge ring is not possible because each pressure segment is assigned its own flat wedge surface.
  • the adjustability of the prestressing force of the sealing segments against the cylinder wall which is possible due to the advantageous development of the invention described, is particularly advantageous in those applications in which the sealing segments are not pressed hydrostatically (by the working pressure) against the cylinder wall.
  • a plate spring acting axially on the wedge ring can function as the spring element, which the sealing elements in the radial direction pre-stressed against the cylinder wall. Because due to the change in the direction of force on the wedge surfaces of the wedge ring, the force of the plate spring acting on the wedge ring in the axial direction is converted into a radial force acting on the lock segments.
  • the plate spring is expediently supported on an axially adjustable prestressing ring. By adjusting the preload ring in the axial direction, the contact pressure of the sealing segments on the cylinder wall can be adjusted and kept constant even when the sealing segments are subject to considerable wear.
  • a pressure relief bore opening in the groove receiving the seal By applying a suitable, in particular a reduced, pressure to the pressure relief bore, one can influence the contact pressure of the sealing segments on the cylinder wall.
  • the pressure relief bore can be connected to the pressure space to be sealed via a pressure reducing device.
  • the corresponding sealing arrangement expediently comprises two radial seals arranged in the same groove, one of which is designed as an outer seal and the other as an inner seal. In this way, an annular space which is connected only to the pressure relief bore can be formed, which can be subjected to a specific pressure in a targeted manner in order to be able to adjust the contact pressure of the sealing segments on the sealing surface.
  • the sealing segments and the lock segments of at least the segment ring facing away from the pressure chamber have at least at their end face lying against the groove wall a circumferential groove are provided. It is particularly preferred to provide two grooves arranged close to one another, which form a common sealing cutting edge. This further reduces the risk of leakage.
  • FIG. 1 in a perspective exploded view
  • FIG. 3 shows an axial section through the piston according to FIG. 2,
  • Fig. 5 explains a preferred development of the sealing and lock segments.
  • the seal shown in FIG. 1 comprises two segment rings 1 and a spring ring 2 acting on both segment rings.
  • Each segment ring consists of eight sealing segments 3 and eight lock segments 4.
  • sealing segments 3 and lock segments 4 alternate with one another. They have the same thickness in the axial direction.
  • the Schroisseg ⁇ elements 4 are wedged outwards, the sealing segments, however, inwards.
  • the two segment rings are constructed to match; however, they are twisted by half a division. Sealing segments 3 and lock segments 4 are dimensioned such that the sealing segments 3 of the two segment rings 1 overlap. Every sealing segment one segment ring is thus in contact with two sealing segments of the other segment ring. As is clearly visible in FIG. 2, this results in a coherent sealing limit.
  • FIG. 1 The position of the sealing segments 3 and the lock segments 4 of the segment rings 1 with respect to one another shown in FIG. 1 corresponds to the installed state.
  • Figures 2 and 3 show that when the seal is inserted into the groove 12 of the piston 6, the lock segments 4 thus do not abut the cylinder wall 7; rather, the tip of each wedge-shaped lock segment 4 maintains a distance from the cylinder wall, so that a channel 5 is formed between the cylinder wall and two adjacent sealing segments 3 and the intermediate lock segment 4.
  • the lock segments 4 project radially inwards over the sealing segments 3.
  • the spring ring 2 is thus only against the lock segments 4 and presses them radially outwards.
  • the sealing segments 3 are spread in the circumferential direction and biased radially outward against the cylinder wall.
  • the main contact force when using the seal shown in Fig. 1 as a piston seal of a reciprocating engine (Fig. 2 and 3) does not provide the spring ring 2, but rather the compressed gas behind (under) the spring ring, as is the case with conventional piston rings Case is.
  • FIG. 3 shows that the gas compressed in front of the piston 6 compresses the two segment rings axially on the one hand, thereby providing Ar with a closed design of the sealing limit and, on the other hand, stepping behind the spring ring 2 and thereby the contact force of the sealing segments 3 on the cylinder wall 7 reinforced.
  • a bore 8 (FIG. 1) is provided in a sealing segment of each of the two segment rings 1, specifically in the area where the two sealing segments overlap.
  • Penetrating adjusting pin 9 serves as an anti-rotation device, which ensures that the predetermined overlap of the sealing segments with respect to each other is maintained.
  • Fig. 4 shows the development of a piston 6 with a circumferential groove, in which a seal comprising two segment rings 1 is inserted.
  • the two segment rings 1 are preloaded against each other in the axial direction by means of a plate spring 31, so that the segments of the segment rings rest firmly on one another in their overlapping areas.
  • Lubricant grooves 10 running in the circumferential direction are provided in the surfaces of the sealing segments 3 abutting the cylinder wall.
  • a lubricant channel 11 opens into each lubricant groove 10.
  • the lubricant channels 11 of the sealing segments 3 of the lower segment ring face the channels 5 of the upper segment ring, which in the manner described above each have two sealing segments 3, the intervening lock segment 4 and the cylinder wall can be limited. This ensures an optimal supply of lubricant to the surfaces of the sealing segments abutting the cylinder wall.
  • the lubricant grooves have a relief effect due to the pressure prevailing here as well as on the back of the sealing segments, i.e. they reduce the contact pressure of the sealing segments against the cylinder wall.
  • the two grooves are arranged so close to one another that they form a common sealing cutting edge
  • the grooves are each on the Side of the sealing segments and Schier ⁇ segments facing away from the work area. That is, the grooves 39 in the right segment ring facing away from the working space are provided in that end face which lies against the side wall of the circumferential groove of the piston, and the grooves in the segment ring facing the working space are in those end faces of the sealing segments and lock segments are provided which abut the right segment ring.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

L'invention a pour objet un moteur à piston alternatif présentant au moins un espace de travail délimité par la paroi du cylindre et au moins un piston monté de façon à osciller à l'intérieur du cylindre. Le piston présente sur sa périphérie au moins une gorge dans laquelle est logé un joint assurant l'étanchéité entre la paroi du cylindre et le piston. Ce joint est composé d'au moins deux anneaux (1) présentant plusieurs segments d'étanchéité (3) et un nombre identique de segments de raccordement (4), ainsi qu'au moins un ressort (2). Les segments d'étanchéité (3) et les segments de raccordement (4) présentent des parties cunéiformes, diamétralement opposées et inclinées vers l'intérieur ou l'extérieur, et sont conçus pour être montés tour à tour à l'intérieur de chaque anneau. Les segments d'étanchéité d'au moins deux anneaux (1) sont imbriqués tour à tour les uns dans les autres et sont précontraints contre la paroi du cylindre, de façon radiale vers l'extérieur, au moyen d'au moins un ressort (2). Un système anti-torsion (9) agissant entre au moins les deux anneaux est également prévu.
EP94913589A 1993-11-19 1994-04-13 Moteur a piston alternatif Withdrawn EP0729554A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4339516 1993-11-19
DE4339516 1993-11-19
PCT/EP1994/001142 WO1995014184A1 (fr) 1993-11-19 1994-04-13 Moteur a piston alternatif

Publications (1)

Publication Number Publication Date
EP0729554A1 true EP0729554A1 (fr) 1996-09-04

Family

ID=6502983

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94913589A Withdrawn EP0729554A1 (fr) 1993-11-19 1994-04-13 Moteur a piston alternatif

Country Status (2)

Country Link
EP (1) EP0729554A1 (fr)
WO (1) WO1995014184A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19630745A1 (de) * 1996-07-30 1998-02-05 Hans Helpap Dichtpaket
DE102005024140B4 (de) 2005-05-23 2007-01-04 Hans Helpap Dichtpaket und Hubkolben mit einem Dichtpaket
WO2009065205A2 (fr) * 2007-11-19 2009-05-28 Andrei Semenov Garniture pour piston
WO2011000073A2 (fr) * 2009-06-29 2011-01-06 Semionov Andrei Groupe piston et cylindre
US10436322B2 (en) 2017-08-09 2019-10-08 Etagen, Inc. Piston sealing ring assemblies
MX2020001580A (es) * 2017-08-09 2020-08-31 Mainspring Energy Inc Instalación de anillo de sellado de pistón que tiene un elemento de cubierta de espacio.
US10443727B2 (en) 2017-08-09 2019-10-15 Etagen, Inc. Sealing ring assemblies configured for pressure locking

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB249945A (en) * 1925-01-09 1926-04-08 Alexander Garden Dunbar Improvements in and relating to pistons
GB375259A (en) * 1929-12-16 1932-06-23 Victor Hanotier Improvements in or relating to pistons
US4986168A (en) * 1989-01-03 1991-01-22 Robert Geffroy Piston and multilayer piston ring set

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9514184A1 *

Also Published As

Publication number Publication date
WO1995014184A1 (fr) 1995-05-26

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