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WO2012037992A1 - Compresseur muni d'un dispositif d'accouplement - Google Patents

Compresseur muni d'un dispositif d'accouplement Download PDF

Info

Publication number
WO2012037992A1
WO2012037992A1 PCT/EP2011/002790 EP2011002790W WO2012037992A1 WO 2012037992 A1 WO2012037992 A1 WO 2012037992A1 EP 2011002790 W EP2011002790 W EP 2011002790W WO 2012037992 A1 WO2012037992 A1 WO 2012037992A1
Authority
WO
WIPO (PCT)
Prior art keywords
lubricant
compressor
piston
compressor according
crankshaft
Prior art date
Application number
PCT/EP2011/002790
Other languages
German (de)
English (en)
Inventor
Joachim Grosskopf
Steffen Krebs
Ralf Stoffels
Original Assignee
Wabco 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 Wabco Gmbh filed Critical Wabco Gmbh
Publication of WO2012037992A1 publication Critical patent/WO2012037992A1/fr

Links

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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/0404—Details, component parts specially adapted for such pumps
    • 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
    • F04B35/002—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 driven by internal combustion engines
    • 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
    • F04B39/02—Lubrication
    • F04B39/0284—Constructional details, e.g. reservoirs in the casing
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/74—Features relating to lubrication

Definitions

  • the invention relates to a compressor for compressed air generation in a vehicle according to the preamble of claim 1.
  • the compressor is separable from or connectable to a drive via a clutch device, for example a disconnect clutch.
  • a generic compressor is known for example from DE 20 2006 019 190 U1.
  • shut-off on compressors has the advantage that the compressor for energy saving by a drive, for example, the drive motor of the vehicle, can be separated when no compressed air generation is required. Without such a shut-off clutch, it was previously common to always run the compressor with the drive motor and in phases in which no compressed air generation was required to switch only pneumatically neutral.
  • the introduction of a shut-off clutch for switching on and off of the compressor has the consequence that the compressor is subjected to a higher wear during connection than during continuous operation. Certain parts of the shut-off are subject to wear and must therefore be lubricated.
  • the invention is based on the object to improve the wear resistance of such a compressor with coupling device.
  • the invention has the advantage of significantly improving the wear resistance of the compressor and thus the durability when used with a coupling device.
  • a common lubricant supply proposed supply channel for both the compressor and the coupling device. This significantly simplifies the supply of the entire unit with lubricant.
  • a throttle point is arranged between a first section of the lubricant supply channel and a second section of this channel. This makes it possible to ensure a suitable supply and distribution of the lubricant both to the parts to be lubricated of the compressor and the coupling device.
  • the passage cross-section of the throttle point is dimensioned such that results in a desired lubricant distribution for the compressor and for the coupling device.
  • the throttle point may be provided directly in front of the coupling device, directly behind the last piston-side lubricant outlet or therebetween. It can also be provided more throttle bodies.
  • Figure 1 shows a two-cylinder compressor in a schematic representation
  • Figure 2 is a Spritzpleuel in sectional view
  • FIG. 5 shows details of an embodiment of the throttle point
  • FIG. 6 shows an interface compressor / coupling device in FIG.
  • Sectional view and Figures 7 and 8 an annular, pot-like receiving element in two
  • FIGS. 9 and 10 further embodiments of a throttle point.
  • FIG. 1 shows a compressor 1 with a compressor housing 2 and a coupling device 3 arranged on the compressor housing 2.
  • the coupling device 3 is designed as a pneumatically actuable shut-off clutch.
  • the coupling device 3 a pneumatic actuating cylinder 19, via the coupling means 18 at pneumatic loading, z.
  • clutch plates or clutch plates are pressed against each other or separable from each other.
  • the coupling device 3 connects a crankshaft 12 of the compressor 1 with a drive shaft of a drive device of a vehicle, not shown in detail, of a vehicle, for example the vehicle engine.
  • the compressor 1 has a first cylinder 8 and a second cylinder 9.
  • a first piston 6 is arranged in the first cylinder 8 .
  • a second piston 7 is arranged in the second cylinder 9.
  • the first piston 6 is connected to the crankshaft 12 via a first connecting rod 10 and corresponding bearings.
  • the second piston 7 is also connected via a second connecting rod 1 1 via corresponding bearings with the crankshaft 12.
  • the storage of the pistons 6, 7 and the crankshaft 12 in the corresponding bearing eyes of the connecting rods 10, 1 1 is shown in Figure 1 for the sake of simplicity only schematically. In practice, suitable sliding or roller bearings are used for this purpose.
  • the cylinders 8, 9 are arranged in a cylinder housing 4 of the compressor 1.
  • the cylinder housing 4 is part of the compressor housing 2.
  • the cylinder housing 4 may also be flanged or attached to the compressor housing 2.
  • valve and control block 5 On the cylinder housing 4, a valve and control block 5 is arranged, for example, the inlet and outlet valves for the compressed air intake and for the compressed air delivery to downstream units such as compressed air reservoir contains.
  • the valve block 5 may be formed in detail, for example, according to DE 197 451 18 A1.
  • the compressor 1 has a lubricant supply.
  • a lubricant for example, oil is used, for example, the engine oil of the vehicle engine.
  • the lubricant supply of the compressor 1 has a lubricant supply port 14 to be connected to the engine oil supply of the vehicle engine. From the lubricant supply port 14, a first
  • the lubricant supply groove 16 is connected to a lubricant supply passage portion 13 which extends in the form of a hollow channel within the crankshaft 12.
  • the channel section 13 communicates with outlet points for the lubricant in the region of the connecting rods 10, 11, which will be explained in greater detail below with reference to FIG.
  • the use of the circulating lubricant supply groove 16 has the advantage that the lubricant can be distributed on the circumference of the crankshaft 12 and, as a result, can be fed into the lubricant passage section 13 relatively quickly and uniformly.
  • the lubricant supply groove 16 may also be arranged in the bearing of the compressor housing 2.
  • the lubricant is usually pressurized and is under a pressure of about 3 to 4 bar. As a result, a lubricant supply is possible regardless of the movement of the compressor, i. even when the compressor is stopped.
  • FIG. 2 shows the connecting rod 1 1 in a sectional view.
  • the cylinder wall 29 of the cylinder 9 is shown, which represents a running surface for the cylinder 9.
  • the connecting rod 1 1 has a connecting rod 25 which is connected to the cylinder 7.
  • Another (lower) connecting rod eye includes the crankshaft 12, which is also shown in the figure 2 in sectional view.
  • a bearing is provided in an advantageous embodiment, which is designed for example as a sliding bearing.
  • a plain bearing has the advantage over a rolling bearing at this point that no seal is required to maintain the oil pressure.
  • a plain bearing is also easier to install.
  • the bearing is not shown explicitly in FIG. 2 for the sake of simplicity of illustration.
  • the passage portion 13 is connected to a radial lubricant portion 20 in the crankshaft 12, which serves to introduce the lubricant into the connecting rod 1 1.
  • the connecting rod 1 1 has in the region of the crankshaft 12 receiving connecting rod on a segment-like expanded portion 21, which forms a channel between the crankshaft and the connecting rod inner side.
  • the extended portion 21 may advantageously be designed as a recess within the connecting rod.
  • the section 21 can also be designed as a groove in the crankshaft 12. It is crucial that a channel for forwarding the lubricant from the channel section 13 to lubricant outlets 22, 23, is formed.
  • the puncture 21 passes the
  • the lubricant outlets 22, 23 are tapered in the direction of the lubricant outlet opening and thus designed in the manner of a nozzle. Due to the overpressure of the lubricant and the nozzle action of the lubricant outlets 22, 23, the lubricant is splashed out of the openings and, as indicated in Figure 2 by the arrow 24, on the cylinder wall 29. This is an early and good lubrication of the cylinder wall ensured with respect to the cylinder, even with temporarily switched off via the coupling device 3 compressor. 1
  • the taper of the lubricant outlets 22, 23 may be continuous or stepped, with a linear or curved contour.
  • FIG. 3 shows the inlet-side connection of the crankshaft 12 to the engine Lubricant Supply Port 14.
  • the lubricant passage section 13 communicates with the circumferential groove 16 of the crankshaft 12.
  • a connection to the lubricant channel 15 is ensured at each rotational angular position of the crankshaft, so that a secure and high throughput of lubricant through the channels 15, 13 is ensured.
  • the lubricant supply channel 13, 15, 16, 20, 21 additionally on a lubricant supply gallery with a plurality of fixedly arranged in the crankcase of the compressor 1 lubricant nozzles.
  • the lubricant nozzles are designed for molding the cylinder bore with the lubricant.
  • the lubricant nozzles can be aligned with your outlet point on the cylinder bore or the cylinder wall 29. As a result, the lubrication of the compressor can be further improved.
  • Figure 4 shows a detail of the cylinder 9 with the piston 7.
  • the piston 7, and possibly also the piston 6, are provided with arranged in circumferential grooves of the piston piston rings 40, 41, 42.
  • the piston rings 40, 41 are formed as compression rings and provide for an air-sealing of the o-above the piston 7 compression space lying opposite the lower crankcase.
  • the piston ring 42 is formed as Olabstreifring.
  • the Olabstreifring should prevent ingress of oil in the lying above the piston 7 compression space.
  • the coating may advantageously contain chromium.
  • the Olabstreifring 42 is formed chromed on its outer surface.
  • the coupling device 3 projects beyond the housing 2 of the compressor 1, that is to say the coupling device is not integrated in the housing, as known from DE 20 2006 019 190 U1.
  • the coupling device 3 protrudes from the housing 2 of the compressor 1 at least with a region containing the coupling means 18, for example the clutch disk or the disk part.
  • the external arrangement of the coupling device offers the advantage of modularity.
  • the compressor according to the invention can therefore be used identically both with and without coupling device. If necessary, the coupling device is merely screwed to the housing 2 of the compressor 1.
  • the compressor according to the invention has the following features:
  • the ⁇ llaysnut in the connecting rod may be pre-cast symmetrical or asymmetrical
  • the groove 16 in the crankshaft can only one side, z. B. on the non-drive side, be provided.
  • a compressor (1) for generating compressed air in a vehicle comprising at least one piston (6, 7), a cylinder (8, 9), a crankshaft (12), a lubricant supply port (14) and a lubricant supply passage (13, 15, 16, 20 , 21), as well as with a coupling device (3), by means of which the crankshaft (12) of the compressor (1) is connectable or separable from a drive device, characterized in that the lubricant supply channel (13, 15, 16, 20, 21 ) provided in at least one inside the compressor (1)
  • Lubricant outlet (22, 23) opens, which is directed at least in certain rotational positions of the crankshaft (12) on a cylinder wall (29) of the cylinder (8, 9).
  • Lubricant supply channel (13, 15, 16, 20, 21) has a through the crankshaft (12) leading channel portion (13).
  • Compressor according to paragraph 2 characterized in that the crankshaft (12) has a circumferential groove (16) communicating with the lubricant supply port (14) with respect to the lubricant guide, which with respect to the lubricant guide with the channel section (13) passing through the crankshaft (12) ) connected is.
  • the groove 16 may also be in the bearing of the crankcase.
  • Compressor according to paragraph 2 or 3 characterized in that the connecting rod (10, 1 1) connecting the piston (6, 7) with the crankshaft (12) has the lubricant outlet (22, 23).
  • Compressor according to paragraph 4 characterized in that the
  • Compressor according to paragraph 5 characterized in that the connecting rod (10, 1 1) as a part of the lubricant supply channel (13, 15, 16, 20, 21) has a recess (21). The groove can also be in the crankshaft.
  • Compressor according to at least one of the preceding paragraphs, characterized in that the lubricant outlet (22, 23) is designed to taper in the direction of the lubricant outlet opening in the manner of a nozzle.
  • Compressor according to at least one of the preceding paragraphs, characterized in that the lubricant supply channel (13, 15, 16, 20, 21) a lubricant supply gallery with a plurality of fixedly arranged in the crankcase of the compressor (1)
  • the lubricant supply 1, 13, 15, 16, 20, 21, 101 from a first section 13, which is located in the region of the pistons 8, 9, to a second section 101, which lies in the region of the coupling device 3.
  • a throttle point 100 is provided between the first portion 13 and the second portion 101, the throttle point 100 may be formed, for example, as a cross-sectional taper of the lubricant supply channel, as a diaphragm, as a diffuser or as a nozzle.
  • the formation of the throttle point through narrow slots between a hub, z. B. a hub which carries the coupling device, and a surrounding bearing sleeve.
  • the slots may be provided on the compressor side or on the coupling side, for example in a part of the coupling device. Also advantageous is the formation of the throttle point by transverse bores in the bushing of the needle roller bearings. A further advantageous embodiment of the throttle point is shown in FIG.
  • FIG. 5 shows the coupling device-side end section of the crankshaft 12, the corresponding part of the first section 13 of the lubricant supply channel provided in the crankshaft 12, the throttle restriction 100, the second section 101 beyond the throttle restriction 100 and a coupling device connected to the second section 101.
  • the throttle point 101 is realized in accordance with FIG. 5 in that an end of a screw 103, not shown in FIG. B. a threaded portion which is screwed into a support member 104 for the coupling device 3, extending into the lubricant supply channel. The end of the screw extends into the lubricant supply channel so far that at least the section connected to the lubricant outlet 102 is covered by it.
  • the flow direction of the lubricant runs through the lubricant supply channel from the lubricant supply connection 14 to the lubricant outlets 22, 23, 102.
  • the flow direction of the lubricant runs through the lubricant supply channel from the lubricant supply connection 14 to the lubricant outlets 22, 23, 102.
  • Lubricant supply port 14 on the side of the first portion 13 of the Lubricant supply channels, ie, as it were in the flow direction before the throttle point. Also possible is the arrangement of the lubricant supply port on the other side of the throttle body 100, ie on the side of the second portion 101 of the lubricant supply channel.
  • FIG. 9 shows a further advantageous realization possibility of the throttling point 100.
  • a screw 90 is screwed into the crankshaft 12 far enough that the lubricant supply channel is reduced with respect to its cross section.
  • the screw 90 may, for. B. so far screwed in that the lubricant supply channel is just not completely penetrated by the screw 90.
  • the screw 90 is completely screwed into the lubricant supply channel, but with respect to its diameter smaller than the diameter of the lubricant supply channel.
  • FIG. 10 shows a further embodiment of the throttle body 100.
  • a screw 91 is screwed into the crankshaft 12.
  • the screw 91 completely penetrates the lubricant supply channel and is screwed into a threaded portion 93 in the crankshaft 12.
  • the screw 91 has at least one bore 92, which serves as a passage for the lubricant from the first portion 13 in the second portion 101 of the lubricant supply channel.
  • the bore 92 thus forms the throttle point 100.
  • a plurality of holes can be provided, for example, two offset by 90 Q holes.
  • FIG. 6 shows an interface region 40 of the compressor 1, which forms an interface to the coupling device 3, in horizontal sectional view.
  • the crankshaft 12 is supported in the housing 2 by a ball bearing 123.
  • an annular, pot-like receiving element 122 is arranged, which is held by a corrugated locking ring 124 in the position shown.
  • the pot-like Receiving element 122 on an annular outwardly flanged edge 127, on which the retaining ring 124 is placed.
  • the pot-like receiving element 122 also serves as a cylinder for a compressed air-operated piston 1 19.
  • the compressed air-actuated piston 1 19 is sealed by seals 135, 136 on the inside and the outside relative to the pot-like receiving element 122.
  • On the outside of the piston 1 19 is still a guide belt 137.
  • the piston 1 19 is used to actuate the coupling device 3.
  • compressed air piston 1 moves 19 in the illustration of FIG 6 to the right and thereby opens the coupling device 3, or the coupling means 18.
  • the crankshaft 12 is separated from the drive shaft 121 connected to the drive means of the clutch device 3, so that the compressor 1 is not driven.
  • the bearing 123 protrudes with a section 126 out of the compressor housing 2.
  • the section 126 also serves as a centering means for the cup-like receiving element 122.
  • the cup-like receiving element 122 with a centering approach, d. H. an annular recess 125, 128, which is adapted in terms of their diameter to the outer diameter of the bearing 123.
  • the bearing 123 serves at the same time for supporting the shaft 121 of the coupling device 3.
  • needle bearings for freewheeling no additional bearings and no further housing required, which promotes a relatively inexpensive implementation of the invention.
  • the coupling device 3 is fastened by means of the collar nut 129 on the crankshaft 12.
  • FIGS. 7 and 8 show the pot-shaped receiving element 122 in a wel Len solution top view ( Figure 7) and in a side view ( Figure 8), in which the cup-shaped receiving element 122 is shown in a sectional view.
  • the pot-shaped receiving element 122 has anti-rotation means 131, 132, which are arranged in the form of projecting recesses in the bottom 140 of the receiving element 122.
  • the anti-rotation means 131, 132 may, for. B. be formed by deep drawing, wherein the anti-rotation means 131, 132 can be formed directly during the deep-drawing process in the production of the receiving element 122.
  • the anti-rotation means 131, 132 are arranged asymmetrically with respect to the circumference of the receiving element 122.
  • the anti-rotation means 131 and the passage opening 80 for the compressed air feedthrough is also shown in FIG.
  • the compressor housing are corresponding complementary, i. opposite, provided to the anti-rotation means 131, 132 shaped recesses, which receive the anti-rotation means 131, 132.
  • the cup-like receiving element 122 represents a substantial improvement in the area of the cut between a compressor and a coupling device.
  • the cup-like receiving element is a multi-functional part, so to speak, which integrates a plurality of design improvements in the interface region 40 with each other.
  • the cup-like receiving element can be produced relatively inexpensively as a metal deep-drawn part. As a result, the invention is inexpensive to implement.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne un compresseur (1) pour la production d'air comprimé dans un véhicule, ledit compresseur comprenant au moins un piston (6, 7), un cylindre (8, 9), un vilebrequin (12), un raccord d'amenée de lubrifiant (14) permettant l'amenée de lubrifiant et un canal d'alimentation en lubrifiant (13, 15, 16, 20, 21, 101) pour l'acheminement et la distribution du lubrifiant du raccord d'amenée de lubrifiant (14) aux raccords de sortie de lubrifiant (22, 23, 102), ainsi qu'un dispositif d'accouplement (3) permettant de relier le vilebrequin (12) du compresseur (1) à un dispositif d'entraînement ou de le séparer de ce dernier. Le compresseur est caractérisé en ce que le canal d'alimentation en lubrifiant (13, 15, 16, 20, 21, 101) s'étend au moins d'une première partie (13) située dans la zone du piston (6, 7) à une seconde partie (101) située dans la zone du dispositif d'accouplement (3), la première partie (13) comportant au moins une sortie de lubrifiant (22, 23) côté piston pour l'alimentation en lubrifiant du piston (6, 7) et la seconde partie (101) comportant au moins une sortie de lubrifiant (102) côté dispositif d'accouplement pour l'alimentation en lubrifiant du dispositif d'accouplement (3), un point d'étranglement (100) étant agencé entre la première partie (13) et la seconde partie (101).
PCT/EP2011/002790 2010-09-22 2011-06-08 Compresseur muni d'un dispositif d'accouplement WO2012037992A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010046031 DE102010046031A1 (de) 2010-09-22 2010-09-22 Kompressor mit Kupplungseinrichtung
DE102010046031.1 2010-09-22

Publications (1)

Publication Number Publication Date
WO2012037992A1 true WO2012037992A1 (fr) 2012-03-29

Family

ID=44509965

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/002790 WO2012037992A1 (fr) 2010-09-22 2011-06-08 Compresseur muni d'un dispositif d'accouplement

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DE (1) DE102010046031A1 (fr)
WO (1) WO2012037992A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015139821A1 (fr) * 2014-03-21 2015-09-24 Wabco Gmbh & Compresseur de gaz et procédé pour faire fonctionner ce compresseur de gaz
DE102017106702B4 (de) * 2017-03-29 2022-02-03 Voith Patent Gmbh Systemgehäuse zur Koppelung eines Kompressorsystems mit einem Antriebsmotor
DE102019126342B4 (de) * 2019-09-30 2024-01-11 Voith Patent Gmbh Druckluftversorgungssystem für ein Kraftfahrzeug

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1322315A (en) * 1971-03-08 1973-07-04 Automotive Prod Co Ltd Friction clutch installations for vehicles
US4561827A (en) * 1983-03-12 1985-12-31 Lucas Industries Limited Air compressor having condition responsive clutch control
GB2162255A (en) * 1984-03-30 1986-01-29 Lucas Ind Plc Multi-plate clutch in an air compressor
DE19745118A1 (de) 1997-10-11 1999-04-15 Wabco Gmbh Druckerzeugungsanlage
DE202006019190U1 (de) 2006-12-15 2008-04-24 Kwd Kupplungswerk Dresden Gmbh Federdruck-Lamellenkupplung für Kompressoren

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3587406A (en) * 1968-07-26 1971-06-28 Copeland Refrigeration Corp Compressor
US8763734B2 (en) * 2007-04-05 2014-07-01 Haldex Brake Corporation Drive through air compressor with cone clutch

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1322315A (en) * 1971-03-08 1973-07-04 Automotive Prod Co Ltd Friction clutch installations for vehicles
US4561827A (en) * 1983-03-12 1985-12-31 Lucas Industries Limited Air compressor having condition responsive clutch control
GB2162255A (en) * 1984-03-30 1986-01-29 Lucas Ind Plc Multi-plate clutch in an air compressor
DE19745118A1 (de) 1997-10-11 1999-04-15 Wabco Gmbh Druckerzeugungsanlage
DE202006019190U1 (de) 2006-12-15 2008-04-24 Kwd Kupplungswerk Dresden Gmbh Federdruck-Lamellenkupplung für Kompressoren

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