EP3387256B1 - Doppelkolbenkompressor einer druckluft-versorgungseinrichtung - Google Patents

Doppelkolbenkompressor einer druckluft-versorgungseinrichtung Download PDF

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Publication number
EP3387256B1
EP3387256B1 EP16820165.5A EP16820165A EP3387256B1 EP 3387256 B1 EP3387256 B1 EP 3387256B1 EP 16820165 A EP16820165 A EP 16820165A EP 3387256 B1 EP3387256 B1 EP 3387256B1
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EP
European Patent Office
Prior art keywords
drive roller
piston compressor
compressor according
axis
double 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.)
Active
Application number
EP16820165.5A
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German (de)
English (en)
French (fr)
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EP3387256A1 (de
Inventor
Klaus Bredbeck
Dieter Frank
Thorsten Weber
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.)
ZF CV Systems Hannover GmbH
Original Assignee
Wabco GmbH
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Publication of EP3387256A1 publication Critical patent/EP3387256A1/de
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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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/01—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being mechanical
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/02—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders arranged oppositely relative to main shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • F01B9/023—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft of Bourke-type or Scotch yoke
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/005—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders with two cylinders
    • 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
    • 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
    • F04B5/00—Machines or pumps with differential-surface pistons
    • F04B5/02—Machines or pumps with differential-surface pistons with double-acting pistons
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics

Definitions

  • the invention relates to a double-piston compressor of a compressed air supply device, having a first pressure stage and a second pressure stage, each having a cylinder with a piston axially beweglich guided therein, wherein the two cylinders are arranged radially opposite to a rotational axis of a drive shaft, wherein the two pistons via a piston rod are rigidly connected to each other and are connected via a slotted guide with the drive shaft in drive connection, wherein the slotted guide has a formed in the piston rod, provided with a slide track and aligned with its cross-sectional plane perpendicular to the axis of rotation of the drive shaft recess, and wherein the slotted guide with a Having the recess engaged, with respect to the axis of rotation of the drive shaft axially parallel and eccentric and rotatably mounted on the drive shaft drive roller.
  • Double piston compressors with two pistons rigidly connected to each other via a piston rod, which are guided axially movably in relation to the axis of rotation of a drive shaft radially oppositely arranged cylinders, have long been known in drive technology different versions.
  • the piston rod via a connecting rod to the drive shaft in drive connection.
  • the connecting rod is on the one hand via a engaging in a first end bore, eccentrically fixed to the drive shaft crankpin and on the other hand via a engaging in a second end bore, longitudinally eccentrically mounted on the piston rod drive pin pivotally connected to the drive shaft and the piston rod.
  • the piston rod is only via a slotted guide with the drive shaft in drive connection.
  • the slotted guide comprises a arranged in the piston rod, provided with two parallel slide tracks, aligned perpendicular to the axis of rotation of the drive shaft recess and a standing with the recess, with respect to the axis of rotation of the drive shaft axially parallel and eccentrically mounted on the drive shaft drive element.
  • a double-piston compressor is described with a slide guide in which the recess of the slide guide is rectangular.
  • the side walls of the recess form the parallel slide tracks, and the two parts of the piston rod are connected to each other via the bottom wall of the recess.
  • the drive element is formed in this slide guide as the outer ring of a roller bearing, which is arranged on a crank pin eccentrically mounted on the drive shaft, and the outer ring is guided in a rollable between the slide tracks of the slide guide.
  • a double-piston compressor with a slide guide in which the recess of the slide guide is formed as a slot-shaped passage opening.
  • the flat inner walls of the recess form the parallel slide tracks, and the two parts of the piston rod are interconnected via end webs, which are executed in the present circular arc, but at the same distance can also be made straight.
  • the drive element is formed in this slide guide as a roller which is mounted directly rotatably mounted on a crank pin eccentrically mounted on the drive shaft and is guided in a rolling motion between the slide tracks of the slide guide.
  • the drive element abuts one of the two parallel slide tracks and, in the event of a reversal of the resulting force direction, bypassing the empty play inevitably present in the slotted guide, merges into the other slide track.
  • a load change of the drive element between the parallel slide tracks it is disadvantageous to a high local load and corresponding signs of wear in the contact region of the drive element with the slide tracks.
  • the present invention has for its object to provide a double piston compressor of the type mentioned, the slide guide is designed such that without additional components and an associated increased space requirement a steady stroke of the piston is ensured whereby discontinuities in the stroke of the piston and wear phenomena are avoided by changing the load of the drive roller.
  • the invention is based on a double-piston compressor of a compressed air supply device, with a first pressure stage, for example a low-pressure stage, and a second pressure stage, for example a high-pressure stage, each having a cylinder with a piston axially guided therein, wherein the two cylinders with respect to a rotational axis of a Drive shaft are arranged radially opposite, wherein the two pistons are rigidly connected to each other via a piston rod and are in driving connection via a slotted guide with the drive shaft, wherein the slotted guide formed in the piston rod, provided with a slide track, and with its cross-sectional plane perpendicular to the axis of rotation Having the drive shaft oriented recess, and wherein the slotted guide one with the recess in engagement, with respect to the axis of rotation of the drive shaft axially parallel and eccentric and rotatable on the drive shaft be has solidified drive roller.
  • the recess of the slide guide is bounded by a closed slide track, which is aligned centrally to a central axis of the piston rod, and on which the drive roller rolls permanently pressed by a resultant pressure force on the two pistons the lateral distance of the slide track, measured perpendicular to the central axis of the piston rod, the maximum of the sum of the double eccentricity and twice the rolling radius of the drive roller corresponds, and that the stroke distance of the slide track, measured parallel to the central axis of the piston rod exceeds twice the rolling radius of the drive roller and the sum of the double eccentricity and twice the rolling radius falls below.
  • the lateral distance here denotes the sum of the maximum distance between the central axis and the slide track measured in each case perpendicular to the central axis.
  • the lateral spacing can therefore also be greater than the cross section of the recess measured perpendicular to the central axis at each point. Rather, the lateral distance is the projection of the maximum diameter of the recess on a plane perpendicular to the center axis.
  • the stroke distance denotes the ideal width of the recess measured along the central axis in an idealized view.
  • the lateral distance of the slide track by an amount ⁇ is less than the sum of the double eccentricity and twice the rolling radius of the drive roller.
  • the drive roller is always in contact with the slide track.
  • the lateral distance is smaller by an amount ⁇ , there is an undersize of the slide track with respect to the enveloping circle caused by the movement the drive roller is formed, so that the drive roller exerts a force on the piston rod not only in the direction of the central axis, but also perpendicular to the central axis of the piston rod.
  • tolerances are compensated in the first place and ensures a permanent contact of the drive roller with the slide track.
  • the compensation of the axial displacement of the piston rod due to the undersized slide track can be provided for example by appropriate seals or a resilient material.
  • the amount ⁇ is in a range of 1% to 5% of the sum of the double eccentricity and twice the rolling radius of the drive roller. More preferably, the amount ⁇ is in a range of 1.5% to 2%.
  • the recess of the slotted guide is preferably limited by a substantially elliptical slide track whose major axis has a length which is at most the sum of the double eccentricity and twice the rolling radius the drive roller divided by the cosine of the inclination angle of the main axis with respect to a perpendicular to the center axis of the piston rod, and whose minor axis has a length which is less than the sum of the double eccentricity and twice the rolling radius of the drive roller, but which is at least so large that the corner radii of the elliptical slide track are larger than the rolling radius of the rolling radius of the drive roller.
  • the main axis H of the elliptical slide track is aligned perpendicular to the central axis of the piston rod.
  • the length L H of the major axis H of the elliptical slide track in this case corresponds at most to the sum of the double eccentricity e and the double rolling radius R R of the drive roller (L H ⁇ 2 * (e + R R )) to the contact of the drive roller in To ensure the side areas of the slide track.
  • the main axis H 'of the elliptical slide track is inclined with respect to a perpendicular to the central axis of the piston rod in the direction of rotation of the drive shaft.
  • the force relationships in the slotted guide can be generally adjusted in a suitable manner.
  • an increase in the lifting height and a phase shift of the lift curve in the direction of late are also compared to the lift curve for a vertical orientation of the slide track causes.
  • the main axis H 'of the elliptical slide track of the slide guide relative to the vertical on the central axis of the piston rod is inclined counter to the direction of rotation of the drive shaft.
  • the angle of inclination ⁇ of the main axis H 'of the slide track should be at most 45 ° with respect to the vertical on the central axis of the piston rod.
  • angles of inclination of at most 30 ° are considered advantageous in order to ensure under all operating conditions that the drive roller is in contact with the slide track.
  • the elliptical slide track of the slide guide is usually formed symmetrically with equal long half-axes of the minor axis N.
  • the elliptical slide track of the slide guide can also be designed asymmetrically with different lengths of semi-axes of the minor axis N '.
  • the main axis H, H 'of the slide track preferably has a length L H.
  • the two pistons are preferably guided over in each case a sealing ring in the cylinders, which are preferably designed as existing of a resilient material sealing sleeves.
  • a sealing ring in the cylinders which are preferably designed as existing of a resilient material sealing sleeves.
  • the radial contact pressure of the drive roller can also be elastically supported by the fact that the radially inner surface of the recess is covered with a resilient layer, which then forms the slide track of the slotted guide in this case.
  • the outer wall of the drive roller is covered with a resilient layer.
  • the sealing rings of the pistons in this case can also be designed as piston rings made of a metal.
  • the resilient layer of the slide track of the slide guide and / or the outer wall of the drive roller is preferably made of rubber.
  • the rubber layer advantageously also the static friction between the drive roller of the slide track and thus a sliding movement of the drive roller can be avoided.
  • At least one middle section of the slideway of the slotted guide can be automatically formed load-dependent bulge.
  • the lifting height of the pressure stroke of the facing piston is reduced depending on the force and thus reduces the mechanical peak load of the slide guide.
  • the wall of the at least one central portion of the slide track is designed to be resilient and spans a cavity of the piston rod, in which the wall of the middle portion of the slide track is recorded at high load.
  • the wall of the at least one central portion of the slide track may also be designed to be flexible and span a cavity of the piston rod, in which at least one pressure spring in contact with the wall in question is arranged, and in which the wall of the middle section bulged at high load the slide track is recorded.
  • the slide track of the slide guide is flat in the longitudinal profile, and that the drive roller has a cylindrical outer wall, with which the drive roller rolled on the slide track. Because of this in the axial direction of the drive shaft even contours on the slide track and the drive roller rotation of the piston rod is caused by the rotation of the piston is superfluous. In addition, thereby an axial displacement of the drive roller relative to the slide track is possible, so that caused by manufacturing tolerances and thermal expansion axial displacements of the drive shaft or the drive roller can be compensated tension-free.
  • the slide track of the slide guide is provided with a circumferential internal toothing, and that the drive roller on its outer wall a External toothing having the same tooth pitch, on the pitch circle of the drive roller rolls on the pitch circle of the internal teeth of the slide track.
  • the manufacturing cost of producing the gears is relatively high.
  • a rotary guide of the piston rod is effected and allows an axial displacement of the drive roller relative to the slide track.
  • the drive roller is rotatably mounted on a bearing pin via a roller bearing or a sliding bearing, which is mounted eccentrically on the drive shaft.
  • the drive roller is preferably formed in this type by an outer ring of the rolling bearing or by a bushing of the sliding bearing.
  • the drive roller is formed as a cylindrical disc and rigidly connected to a central bearing pin, which is rotatably mounted via a roller bearing or a plain bearing in an eccentrically arranged on the drive shaft bearing bore.
  • the bearing pin of the drive roller or the drive roller itself is provided with a central outer bearing shaft, which radially externally mounted on a housing side via a roller bearing or a plain bearing, coaxial with the axis of rotation of the drive shaft aligned bearing pin is supported.
  • a trained according to the invention as a basic design viewable first embodiment of a double piston compressor 1.1 a compressed air supply device is in Fig. 1 in a longitudinal middle section and in 1a shown in a cross-sectional view.
  • the double-piston compressor 1.1 has a first pressure stage 2 designed as a low-pressure stage and a second pressure stage 3 designed as a high-pressure stage, each having a cylinder 4, 7 with a piston 5, 8 guided axially movably therein.
  • the two pistons 5, 8 are each sealed by a sealing ring 6, 9, which are preferably designed as an existing of an elastic material such as rubber sealing sleeves, relative to the associated cylinder 4, 7 and slidably guided in this.
  • the two cylinders 4, 7 are arranged with respect to a rotational axis 13 of a drive shaft 12 radially opposite one another.
  • the two pistons 5, 8 are connected rigidly to one another via a piston rod 10 and are in drive connection via a slotted guide 14. 1 to the drive shaft 12.
  • the slide guide 14.1 comprises a arranged in the piston rod 10, bounded by a closed elliptical slide track 16.1 and with its cross-sectional plane perpendicular to the rotation axis 13 of the drive shaft 12 aligned recess 15.1, and one with the slide track 16.1 of the recess 15.1 in engagement, with respect to the axis of rotation 13 of the drive shaft 12 axially parallel and eccentric and rotatably mounted on the drive shaft 12 drive roller 17th
  • the recess 15.1 and thus also the slotted guide 14.1 are aligned centrally to a central axis 11 of the piston rod 10.
  • the main axis H of the elliptical slide track 16.1 has a length L H , which is slightly less than the sum of the double eccentricity e and the double rolling radius R R of the drive roller 17 (see also Fig. 13a-d ; with reference to the Fig. 13a-d the effect of underrun will be displayed more accurately). Since the inclination of the slide track 16.1 relative to a vertical 23 on the central axis 11 of the piston rod 10 in the embodiment according to the FIGS.
  • the minor axis N of the elliptical slide track 16.1 has a length L N which is less than the sum of the double eccentricity e and twice the rolling radius R R of the drive roller 17, so that the formula L N ⁇ 2 * (e + R R ) applies, however, this length L N is at least so great that the corner radii R E of the elliptical slide track 16.1 are greater than the rolling radius R R of the drive roller 17 (R E > R R ).
  • the drive roller 17 is presently formed by the outer ring 19 of a roller bearing 18, which is arranged on a eccentrically mounted eccentrically on the drive shaft 12 bearing pin 20 e.
  • the slide track 16.1 of the slotted guide 14.1 is flat in the longitudinal profile and the drive roller 17 has a cylindrical outer wall over which the drive roller 17 rolls on the slide track 16.1, also an axial displacement of the drive roller 17 relative to the slide track 16.1 is possible, so that caused by manufacturing tolerances and thermal expansion axial displacements of the drive shaft 12 and the drive roller 17 can be compensated tension-free.
  • Fig. 1b is the lift curve z H ( ⁇ ) of the piston 5, 8 and the piston rod 10 of the double piston compressor 1.1 shown for one revolution of the drive shaft 12, wherein the rotation angle of the drive shaft 12 is denoted by ⁇ and the direction of rotation of the drive shaft 12 corresponding to that in the cross-sectional view of Fig. 1a pictured direction of rotation arrow 21 is assumed in a clockwise direction.
  • the bearing pin 20 and the drive roller 17 are shown in the 90 ° position of the drive shaft 12.
  • the lifting height of the piston 5, 8 is in the diagram of Fig. 1b denoted by z H , wherein the stroke direction of the pistons 5, 8 corresponding to the in Fig.
  • a second embodiment according to the invention of a double piston compressor 1.2 of a compressed air supply device is in Fig. 2 in a longitudinal middle section and in Fig. 2a shown in a cross-sectional view.
  • Fig. 2b Shown stroke lift z H ( ⁇ ) of the piston 5, 8 and the piston rod 10 of the double piston compressor 1.2 has a modified sinusoidal course, due to the inclined in the direction of rotation 21 of the drive shaft 12 arrangement of the elliptical slide track 16.2 a phase shift in the late and over the lifting height z H_ max with vertical arrangement of the slide track 16.1 according to Fig. 1 and 1a having exceeding lifting height.
  • Fig. 2b also the lift curve z H ( ⁇ ) of the piston 5, 8 of the double piston compressor 1.1 according to the FIGS. 1 and 1a out Fig. 1b drawn as a dash-dot curve.
  • FIG. 3 A third embodiment of a double-piston compressor 1.3 of a compressed air supply device according to the invention is shown in FIG Fig. 3 in a longitudinal middle section and in Fig. 3a shown in a cross-sectional view.
  • This embodiment of the double piston compressor 1.3 differs by a differently modified arrangement of the slide guide 14.3 of the double piston compressor 1.1 according to Fig. 1 ,
  • the recess 15.3 with the elliptical slide track 16.2 relative to the vertical 23 on the central axis 11 of the piston rod 10 by an inclination angle of ⁇ - 30 ° against the direction of rotation 21 of the drive shaft 12 is arranged rotated.
  • FIG. 3b Shown stroke lift z H ( ⁇ ) of the piston 5, 8 and the piston rod 10 of the double piston compressor 1.3 has a modified sinusoidal shape, due to the opposite direction of rotation 21 of the drive shaft 12 inclined arrangement of the elliptical slide track 16.2 a phase shift in the direction early and one over the lifting height z H_ max with vertical arrangement of the slide track 16.1 according to Fig. 1 and 1a having exceeding lifting height.
  • Fig. 3b also the lift curve z H ( ⁇ ) of the piston 5, 8 of the double piston compressor 1.1 according to the FIGS. 1 and 1a out Fig. 1b drawn as a dash-dot curve.
  • a fourth embodiment of a double-piston compressor 1.4 according to the invention of a compressed air supply device is in Fig. 4 in a longitudinal middle section and in Fig. 4a shown in a cross-sectional view.
  • This embodiment of the double piston compressor 1.4 differs by a modified design of the slotted guide 14.4 of the double piston compressor 1.1 Fig. 1 , While the elliptical slide track 16.1, 16.2 is executed symmetrically in the previously described slide guides 14.1, 14.2, 14.3, which is in the FIGS. 4 and 4a Shown guide 14.4 shown in the recess 15.3 with different lengths L N / 2, L N '/ 2 of the two semi-axes of the minor axis N' of the elliptical slide track 16.3 now formed asymmetrically.
  • the semi-axis of the minor axis N 'facing the piston 8 of the high-pressure stage 3 has a length L N ' / 2 reduced relative to the length L N / 2 of the other semi-minor axis of the minor axis N '(L N ' / 2 ⁇ L N / 2).
  • FIG. 4b The in the diagram of Fig. 4b illustrated lifting curve z H ( ⁇ ) of the piston 5, 8 and the piston rod 10 of the double piston compressor 1.4 has a respect to the central axis asymmetric sinusoidal course, due to the reduced length L N '/ 2 of the piston 8 of the high-pressure stage 3 facing half axis of the minor axis N 'of the elliptical slide track 16.3 has an increased lifting height z H_max ' in the stroke direction 22.
  • Fig. 4b also the lift curve z H ( ⁇ ) of the piston 5, 8 of the double piston compressor 1.1 according to the FIGS. 1 and 1a out Fig. 1b drawn as a dash-dot curve.
  • Az H_max difference of heights Az z H_max H_max '- such H_max located.
  • Fig. 5 is a fifth embodiment of a double piston compressor according to the invention 1.5 a compressed air supply device shown in a fragmentary longitudinal center section.
  • the slotted guide 14.5, the elliptical slide track 16.4 is occupied with a correspondingly enlarged recess 15.4 with a preferably made of rubber elastic layer 24.
  • the lateral radial contact force of the drive roller 17 generated by the undersize of the main axis H of the elliptical slide track 16.4 in conjunction with a small radial displacement of the piston rod 10 in addition to the sealing collars 6, 9 supported elastically via the resilient layer 24.
  • a compressed air supply device is at the local slide guide 14.6 in the recess 15.1, the drive roller 25 'with a corresponding reduction of its outer diameter with a preferably made of rubber elastic layer 24' occupied.
  • the drive roller 25 ' is formed as an alternative to the above-described embodiment of the drive roller 17 by way of example.
  • the drive roller 25 ' is formed as a cylindrical disc and rigidly connected to a central bearing pin 26, the is mounted rotatably in a about the eccentricity e eccentrically arranged on the drive shaft 12 bearing bore 28 via a sliding bearing 27.
  • FIGS. 7 and 8th are a seventh and an inventive eighth embodiment of a double piston compressor 1.7, 1.8 a compressed air supply device each shown in a fragmentary cross-sectional view in which the middle in their longitudinal direction middle sections of the elliptical slide track 16.5 of the respective slide guide 14.7, 14.8 in the recesses 15.5 of the piston rod 10th each self-dependent load-dependent bulge formed.
  • the slotsted guide 14.7 according to Fig. 7 are the walls 29 of said middle portions of the slide track 16.5 spring-elastic and each span a cavity 30 of the piston rod 10.
  • the walls 31 of the middle sections of the slide track 16.5 are elastically bent and each span a cavity 30 'of the piston rod 10, in each of which a standing with the relevant wall 31 in contact, in this case designed as a bow spring compression spring 32 is arranged. Due to the possible bulge of the said central portions of the slide track 16.5, the lifting height of the pressure stroke of each facing piston 5, 8 is reduced depending on the force and thus reduces the peak load of the slide guide 14.7, 14.8.
  • Fig. 9 9 shows a ninth embodiment of a compressed air supply device according to the invention by internal teeth 33 of the slot 15.6 delimiting slide track 16.6 and an external toothing on the drive roller 17 'of the slide guide 14.9.
  • the slide track 16.6 of the slotted guide 14.9 is provided with a circumferential internal toothing 33
  • the drive roller 17 ' has on its by the outer ring 19' of a roller bearing 18 'outer wall formed a toothing 34 with the same tooth pitch, on the pitch circle of the drive roller 17' on the pitch circle of the internal teeth 33 of the slide track 16.6 rolls.
  • a compressed air supply device is shown in a fragmentary longitudinal center section, in which the drive roller 17 "and connected to this drive shaft 12 via the slotted guide 14.10 are axially guided in the piston rod 10.
  • the slotted guide 14.10 is the recess 15.7 limiting link path 16.7 provided with a circumferential inner web 35, and the drive roller 17 "has on its outer ring 19" of a roller bearing 18 "formed radial outer wall a circumferential annular groove 36, in which the inner web 35 of the slide track 16.7 axial guidance of the drive roller 17 "engages.
  • FIGS. 11 and 12 are an eleventh embodiment of the invention and a twelfth embodiment of the invention of a double piston compressor 1.11, 1.12 a compressed air supply device each shown in a fragmentary longitudinal center section, in which the drive roller 17, 25 and the drive shaft 12 are each provided with an additional storage.
  • the double piston compressor 1.11 according to Fig. 11 have the drive roller 17 and the recess 15.1 limiting link path 16.1 of the slotted guide 14.11 from the FIGS. 1 to 4 and 7 and 8 known construction.
  • the bearing pin 20 'of the drive roller 17 is provided with a central, axially outer bearing shaft 37 which is radially outwardly supported by a roller bearing 38 on a housing side, coaxially aligned with the axis of rotation of the drive shaft 12 bearing pin 39.
  • the double piston compressor 1.12 corresponds to the drive roller 25 without the resilient layer 24 'of in Fig. 6 shown construction.
  • the drive roller 25 is now itself with a central, axially outer bearing shaft 40 is provided with this slide guide 14.12, which is supported by a roller bearing 38 radially outwardly on the housing side fixed, coaxial with the axis of rotation 13 of the drive shaft 12 aligned bearing pin 39.
  • FIGS. 13a to 13d illustrate again the state when an undersize of the major axis H of the elliptical slide track 16 is provided, and thus the side distance of the slide track 16 by an amount ⁇ is less than the sum of the double eccentricity e and the double rolling radius R R of the drive roller 17th
  • FIGS. 13a to 13d For example, the elements with the same reference numerals as shown in the first twelve embodiments are shown, wherein the trailing numerals are omitted and insofar as, for example, the number 1 denotes the double piston compressor without a suffix for certain embodiments, since the schematic representations in the FIGS. 13a to 13d refer equally to all embodiments.
  • the recess 15 is shown as a horizontally oriented ellipse with a horizontally oriented main axis H.
  • the center axis of the piston is denoted by 11, and a center axis of the double piston compressor 1 is designated 41.
  • Fig. 13a the axis of rotation 13 of the drive shaft 12 cuts (in the schematic FIGS. 13a-d not shown) the center axis 41.
  • the drive roller 17 is guided along a path and describes an enveloping circle 42.
  • the enveloping circle 42 is circular, and as shown in FIGS FIGS. 13a-d larger than both the major axis H and the minor axis N of the slide track 16. Therefore, the drive roller 17 presses in the in Fig. 13a shown position in which it is rotated to an angle of 270 ° with respect to the top dead center, the piston rod 10 with respect to Fig.
  • the axial displacement of the piston rod 10 by the amount ⁇ / 2 is compensated in this illustration by the sealing rings 6, 9, which are elastic. In other embodiments, such as the embodiment of the Fig. 5 or Fig. 6 , It is also conceivable to compensate for the compensation of the axial displacement by the amount .DELTA. / 2 through the resilient layer 24, 24 '.
  • the drive roller 17 is permanently in contact with the slide track, even if manufacturing tolerances are taken into account. It has a certain pressure permanently to the slide track 16, and a discontinuity, ie a lift in the drive roller 17 of the slide track 16 does not take place even when the double piston compressor 1 is exposed to vibrations or shaking.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
EP16820165.5A 2015-12-08 2016-12-07 Doppelkolbenkompressor einer druckluft-versorgungseinrichtung Active EP3387256B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102015015948 2015-12-08
DE102016013739.8A DE102016013739A1 (de) 2015-12-08 2016-11-17 Doppelkolbenkompressor einer Druckluft-Versorgungseinrichtung
PCT/EP2016/002060 WO2017097415A1 (de) 2015-12-08 2016-12-07 Doppelkolbenkompressor einer druckluft-versorgungseinrichtung

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EP3387256A1 EP3387256A1 (de) 2018-10-17
EP3387256B1 true EP3387256B1 (de) 2019-10-23

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US (1) US10859075B2 (zh)
EP (1) EP3387256B1 (zh)
JP (1) JP6905511B2 (zh)
KR (1) KR102016677B1 (zh)
CN (1) CN108026911B (zh)
DE (1) DE102016013739A1 (zh)
WO (1) WO2017097415A1 (zh)

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DE102019104856A1 (de) * 2019-02-26 2020-08-27 Wabco Gmbh Kolbenkompressor
CN110043440A (zh) * 2019-05-29 2019-07-23 王湫锂 平衡型增压泵驱动机构
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CN113464393A (zh) * 2021-07-28 2021-10-01 苏州力奇研发有限公司 柱塞泵及高压清洗机
CN113565730A (zh) * 2021-08-26 2021-10-29 瑞立集团瑞安汽车零部件有限公司 一种新型往复容积式空气压缩机
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Also Published As

Publication number Publication date
KR20180039653A (ko) 2018-04-18
EP3387256A1 (de) 2018-10-17
US20180266406A1 (en) 2018-09-20
JP2018536791A (ja) 2018-12-13
US10859075B2 (en) 2020-12-08
CN108026911B (zh) 2019-07-05
KR102016677B1 (ko) 2019-10-23
WO2017097415A8 (de) 2018-03-01
CN108026911A (zh) 2018-05-11
JP6905511B2 (ja) 2021-07-21
DE102016013739A1 (de) 2017-06-08
WO2017097415A1 (de) 2017-06-15

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