EP0336893A1 - Compresseur à plongeur - Google Patents

Compresseur à plongeur Download PDF

Info

Publication number
EP0336893A1
EP0336893A1 EP89810220A EP89810220A EP0336893A1 EP 0336893 A1 EP0336893 A1 EP 0336893A1 EP 89810220 A EP89810220 A EP 89810220A EP 89810220 A EP89810220 A EP 89810220A EP 0336893 A1 EP0336893 A1 EP 0336893A1
Authority
EP
European Patent Office
Prior art keywords
piston
oil
plunger
recess
compressor according
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
EP89810220A
Other languages
German (de)
English (en)
Other versions
EP0336893B1 (fr
Inventor
Eduard Müller
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.)
Burckhardt Compression AG
Original Assignee
Maschinenfabrik Burckhardt AG
Maschinenfabrik Sulzer Burckhardt 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 Maschinenfabrik Burckhardt AG, Maschinenfabrik Sulzer Burckhardt AG filed Critical Maschinenfabrik Burckhardt AG
Priority to AT89810220T priority Critical patent/ATE76485T1/de
Publication of EP0336893A1 publication Critical patent/EP0336893A1/fr
Application granted granted Critical
Publication of EP0336893B1 publication Critical patent/EP0336893B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid

Definitions

  • the invention relates to a plunger compressor with at least one piston which can be moved back and forth in a cylinder via a crankshaft and a connecting rod, which has a guide part which faces the crank chamber and is guided in a lubricated cylinder section, and a working part which is offset therefrom and is designed as a dry-running gas seal part, in particular as a labyrinth piston which delimits a compression space in the cylinder, oil-wiping means being provided in the movement area of the guide part and in the cylinder, outside the movement area of the working part, a leak discharge space connected to a low-pressure space for discharging leakage gas emerging from the compression space and leakage oil emerging from the crank chamber is provided.
  • the invention has for its object to provide a particularly improved in this regard, further developed plunger compressor, in which oil particles adhering to the guide part are reliably detected and reliably kept away from the portion of the cylinder surface assigned to the working part.
  • this object is achieved in that in a longitudinal section of the piston reaching the area of the leakage discharge space in the top dead center position of the piston, at least one annular groove-like depression for catching an oil film that may creep along the surface of the guide part and for dispensing the oil collected into the leakage discharge space and / or is provided in the lubricated cylinder section.
  • the ring-groove-like depression provided according to the invention retains oil particles adhering to the guide part outside the length of the piston which extends over the range of movement of the working part until oil drops which can be separated off are formed. Due to the maximum deceleration or acceleration of the piston occurring during the respective reversal of the piston movement, these oil drops are thrown into the leakage removal space in the top dead center position of the piston and onto the lubricated running surface of the cylinder assigned to the guide part in the bottom dead center position.
  • the plunger compressor according to FIG. 1 has a crankshaft 2, which is mounted in a crankcase 1 and has a crank pin 3, to which a connecting rod 4 is articulated.
  • the other end of the connecting rod 4 is articulated via a piston pin 5 to a piston 6, which is sealingly guided in a cylinder 7 connected to the crankcase 1 and arranged with a horizontal longitudinal axis L.
  • a cylinder 7 connected to the crankcase 1 and arranged with a horizontal longitudinal axis L.
  • two corresponding ones for example opposite one another, can also be used arranged cylinders or more, for example three or four star-shaped cylinders 7 may be provided, each containing a corresponding piston 6 which can be driven via the common crankshaft and a connecting rod.
  • the cylinder 7, which is open against the crankcase 1, is closed at its end facing away from the crankcase 1 by an end wall 8 of a cylinder head 10, which contains a suction chamber 11 and a pressure chamber 12.
  • the suction chamber 11 is connected through an inlet opening 13 to a suction line (not shown) for the gas to be compressed, while the pressure chamber 12 is connected through an outlet opening 14 to a pressure line (not shown) for the compressed gas.
  • the piston 6 has a guide part 6a facing the crankcase 1 and a working part 6b which is connected to the crankcase 1 via a stepped middle piston section 6c and faces the cylinder head and which delimits a compression space 15 with the end wall 8.
  • the compression chamber 15 can be connected to the suction chamber 11 via a suction valve 17 arranged in the end wall 8 and a corresponding pressure valve 18 to the pressure chamber 12.
  • the piston 6 can be moved back and forth via the crankshaft 2, which can be driven according to arrow 16, between the "upper" dead center position shown in full lines and the "lower” dead center position 6 'indicated by dash-dotted lines in FIG. 1, the guide part 6a in the corresponding cylinder section 7a guided and lubricated by spray oil supplied from the crankcase 1.
  • the guide part 6a is provided with scraper rings 20, through which most of the oil supplied is returned to the crankcase 1.
  • the oil that accumulates between the scraper rings 20 can be drained into the interior of the guide part 6a through passage openings (not shown) provided in the guide part 6a.
  • the working part 6b is a dry run
  • the gas seal part is embossed by being provided on its outer circumference with labyrinth seal grooves which form a contactless seal with the cylinder section 7b surrounding them.
  • a leak discharge space 21 is formed, which extends like a ring in the cylinder space and which is connected via an outlet duct 22 to a space, not shown, in which a lower pressure prevails than in the leak discharge space 21.
  • the outlet duct 22 can be connected to the outlet duct 22.
  • a discharge line, not shown, may be connected, which is intended for discharging leakage gas emerging from the compression space 15 via the labyrinth seal and leakage oil not detected by the scraper rings 20.
  • the leakage discharge space 21 can also be connected to the crankcase 1 via a pressure compensation line 24 connected to a passage 23 of the cylinder 7, thereby preventing a pressure drop across the scraper rings 20. Accordingly, even at high piston speeds, the wear on the guide part 6a and / or in the cylinder section 7a can be kept low.
  • the piston 6 is in a section A adjoining the guide part 6a, which reaches the area of the leakage discharge space 21 when the piston 6 is at the top dead center, with at least two, as shown three, annular groove-like depressions 25, 25a arranged one behind the other in the axial direction of the piston 6 and 25b.
  • the recess 25a or 25b closer to the working part 6b is made with a greater depth T than the recess 25 or 25a adjacent to it in the direction towards the guide part 6a.
  • the depressions 25, 25a, 25b are laterally delimited by rib-like elevations 26, 26a, 26b, which each protrude beyond the adjacent piston section 6c and each with one extending over its circumference sharp edge 27 are provided.
  • the depressions 25, 25a, 25b each have two flanks 29 and 30 which run essentially parallel to one another.
  • the depressions 25, 25a, 25b can furthermore be provided with inserts 28 which are intended for the temporary storage of oil particles and which are omitted in FIG. 1 for the purpose of simplifying the illustration.
  • the inserts 28 each consist of a material suitable for collecting the oil particles, for example steel wool, which enables the oil particles to be combined into separable oil drops and which at the same time is sufficiently permeable to allow oil to flow into the recesses 25, 25a and 25b from above or from the side to let gravity flow down.
  • the elevations 26, 26a, 26b can be formed by flexible lamella-like wall parts of small wall thickness, which are elastically deformable when the piston 6 is moved back and forth in the sense of a narrowing or widening of the depressions 25, 25a, 25b.
  • the depressions 25, 25a, 25b prevent the cylinder section 7b assigned to the working part 6b from being wetted by oil adhering to the guide part 6a, in that an oil film that may creep along the surface of the guide part 6a at least in the final phase of the left in FIG. 1 Compression stroke of the piston 6, which runs on the right, reaches the recess 25 and is retained there until droplets which can be separated form from the oil particles and which, when the movement is reversed in the top dead center position of the piston 6 shown in FIG. 1, from the recess 25 into the leak discharge space 21 , and if necessary can be thrown onto the lubricated running surface of the cylinder section 7a in the bottom dead center position.
  • the flexibly designed elevations 26, 26a and 26b have the tendency to increase the volume of the depressions 25, 25a and 25b and thus to retain the oil contained therein.
  • these elevations 26, 26a and 26b in the bottom dead center position 6 'of the piston 6 have the tendency to reduce the volume of the depressions 25, 25a, 25b and thus to press the oil out of them.
  • an embodiment is also possible in which only a single depression 25 is provided in the section A of the piston 6 which reaches the area of the leakage discharge space 21 and in which a braid made of steel wool is arranged as an insert 28 for collecting oil particles.
  • the elevation 26 delimiting the recess 25 can be formed by a rigid wall part, so that the pumping action described above does not occur.
  • the depressions 25, 25a, 25b can be designed with flanks 29, 30 which are inclined with respect to the longitudinal axis L of the piston 6 and which form an acute angle ⁇ with the longitudinal axis L, the apex S of which points towards the working part 6b.
  • the major part of the oil collected can be retained in the top dead center position of the piston 6 in the depressions 25, 25 a and 25 b inclined in the manner described and can be easily thrown out of these in the bottom dead center position 6 'of the piston 6 against the cylinder section 7 a.
  • the elevations 26, 26a and 26b can be formed by rigid or flexible wall sections. 3
  • the angle ⁇ is approximately 60 °. They are also executions possible with any other angles ⁇ equal to or less than 90 °, the lower limit value of the angle ⁇ being essentially given by design.
  • the depressions 25, 25a and 25b can be delimited by loose, disc-shaped ring elements 31, which are fastened at a distance from one another on the piston part 6c of the piston 6 by means of spacer rings 32, 32a, 32b and a retaining ring 33.
  • the working part 6b is connected to the piston section 6c by screws 34.
  • sealing rings 36 made of a self-lubricating material suitable for dry running, e.g. Teflon or graphite can be provided, through which the working part 6b is sealingly guided in the cylinder section 7b.
  • the ring elements 31 can be made from rigid or from thin, flexible sheet metal or plastic parts, which enable the selective deposition described above.
  • the dimensions and the number of depressions 25, 25a, 25b can be optimized and, if necessary, changed in a simple manner, without complex machining of the piston 6.
  • the oil scraper rings 20 assigned to the guide part 6a are fixedly arranged in a support ring 37 which is inserted into an annular groove 38 provided in the cylinder section 7a of the cylinder 7 divided in the region of this annular groove 38.
  • the annular groove 38 is connected to the outlet channel 22 connected to the leakage discharge space 21.
  • the support ring 37 is provided with through openings 40 through which leakage oil and leakage gas can be discharged into the outlet channel 22.
  • the working part 6b has a larger diameter than the guide part 6a, which with a conical shoulder 44 in the Piston section 6c merges.
  • the recesses 25, 25a and 25b provided in this embodiment are delimited by the shoulder 44 and by ring elements 41 designed in the shape of a cone shell, which are fastened by corresponding cone-shaped spacer rings 42, 42a 42b and a retaining ring 43 at intervals on the piston section 6c.
  • ring elements 41 designed in the shape of a cone shell, which are fastened by corresponding cone-shaped spacer rings 42, 42a 42b and a retaining ring 43 at intervals on the piston section 6c.
  • the flanks 29, 30 of the depressions 25, 25a and 25b which are inclined with respect to the longitudinal axis L of the piston 6 are formed.
  • the ring elements 41 can also be formed by rigid or by flexible sheet metal or plastic parts.
  • the depressions 25, 25a and 25b can be arranged at such short intervals, e.g. less than 1 mm, flanks 29, 30 running from each other, that between these flanks 29, 30 there is a capillary action, through which the introduction of the oil particles adhering to the guide part 6a into the recesses 25, 25a and 25b is promoted and through which the Oil particles are retained in the depressions 25, 25a and 25b until the oil drops which form are spun off.
  • the depressions 25, 25a and 25b with the corresponding elevations 26, 26a and 26b can also be formed on a common ring element 35 which can be fastened to the piston 6.
  • the ring element 35 can be made of metal or, as shown, of a plastic and can be made in one or more parts.
  • the recesses 25, 25a and 25b can also be embodied with correspondingly small distances between the flanks 29, 30, which are suitable for producing a capillary effect, in the case of the embodiments 1 to 4 and 6, it being unnecessary to use inserts 28.
  • the depressions 25, 25a and 25b are made with larger distances between their flanks 29, 30 and are provided with corresponding inserts 28. Designs are also possible in which the successive depressions 25, 25a and 25b, in particular if they are delimited by rigid wall parts, have essentially the same depths T.
  • profiled ring elements 45 can be used, as shown in FIGS. 7 and 8, which also join to the opposite flank 29 or 30 of the recess in question, radially extending bead-like elevations 46 are provided, the heights H of which determine the distance to the correspondingly adjacent ring element 45.
  • Corresponding ring elements can also be offset with other circumferentially, e.g. wave-like or wart-like elevations.
  • corresponding ring elements 47 can also be provided with bolt-like spacers 48 or similar spacers.
  • insert 28 can be used instead of steel wool.
  • one made of glass fibers or another suitable material, e.g. a plastic, formed insert 28 can be used.
  • the associated insert 28 can also be made from an oil-permeable ceramic material or a correspondingly permeable sintered metal.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
EP89810220A 1988-04-08 1989-03-21 Compresseur à plongeur Expired - Lifetime EP0336893B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89810220T ATE76485T1 (de) 1988-04-08 1989-03-21 Tauchkolbenkompressor.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1311/88 1988-04-08
CH1311/88A CH674550A5 (fr) 1988-04-08 1988-04-08

Publications (2)

Publication Number Publication Date
EP0336893A1 true EP0336893A1 (fr) 1989-10-11
EP0336893B1 EP0336893B1 (fr) 1992-05-20

Family

ID=4207471

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89810220A Expired - Lifetime EP0336893B1 (fr) 1988-04-08 1989-03-21 Compresseur à plongeur

Country Status (7)

Country Link
EP (1) EP0336893B1 (fr)
JP (1) JPH01285678A (fr)
AR (1) AR240189A1 (fr)
AT (1) ATE76485T1 (fr)
BR (1) BR8901639A (fr)
CH (1) CH674550A5 (fr)
DE (1) DE58901449D1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4006156A1 (de) * 1990-02-27 1991-08-29 Knorr Bremse Ag Kolbenverdichter, insbesondere fuer die drucklufterzeugung in kraftfahrzeugen
GB2400891A (en) * 2003-04-23 2004-10-27 Boc Group Plc Dry pump oil sump and lubricant conduits
DE102012006780A1 (de) * 2012-04-03 2013-10-10 Thomas Magnete Gmbh Hubkolbenpumpe mit durchströmtem Gleitlager

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008042645A1 (de) * 2008-10-07 2010-04-08 Robert Bosch Gmbh Brennraumdrucksensor

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1408638A (en) * 1920-06-03 1922-03-07 Ingersoll Rand Co Compressor
GB771334A (en) * 1954-12-22 1957-03-27 Friedrich Hagans Improvements in single acting piston machines

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1408638A (en) * 1920-06-03 1922-03-07 Ingersoll Rand Co Compressor
GB771334A (en) * 1954-12-22 1957-03-27 Friedrich Hagans Improvements in single acting piston machines

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4006156A1 (de) * 1990-02-27 1991-08-29 Knorr Bremse Ag Kolbenverdichter, insbesondere fuer die drucklufterzeugung in kraftfahrzeugen
GB2400891A (en) * 2003-04-23 2004-10-27 Boc Group Plc Dry pump oil sump and lubricant conduits
DE102012006780A1 (de) * 2012-04-03 2013-10-10 Thomas Magnete Gmbh Hubkolbenpumpe mit durchströmtem Gleitlager
DE102012006780B4 (de) * 2012-04-03 2018-03-15 Thomas Magnete Gmbh Elektromagnetische Hubkolbenpumpe mit Kolbengleitlager, wegen der Pumpwirkung einer gerichteten Schleppströmung durchflossen

Also Published As

Publication number Publication date
DE58901449D1 (de) 1992-06-25
ATE76485T1 (de) 1992-06-15
BR8901639A (pt) 1989-11-21
JPH01285678A (ja) 1989-11-16
AR240189A1 (es) 1990-02-28
EP0336893B1 (fr) 1992-05-20
CH674550A5 (fr) 1990-06-15

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