EP1548280A1 - Compresseur à piston - Google Patents

Compresseur à piston Download PDF

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Publication number
EP1548280A1
EP1548280A1 EP04030336A EP04030336A EP1548280A1 EP 1548280 A1 EP1548280 A1 EP 1548280A1 EP 04030336 A EP04030336 A EP 04030336A EP 04030336 A EP04030336 A EP 04030336A EP 1548280 A1 EP1548280 A1 EP 1548280A1
Authority
EP
European Patent Office
Prior art keywords
piston
valve
crankshaft
reciprocating compressor
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
EP04030336A
Other languages
German (de)
English (en)
Other versions
EP1548280B1 (fr
Inventor
Peter Dr.-Ing. Kreuter
Armin Dipl.-Ing. Zoschke
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.)
Meta Motoren und Energie Technik GmbH
Original Assignee
Meta Motoren und Energie Technik 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 Meta Motoren und Energie Technik GmbH filed Critical Meta Motoren und Energie Technik GmbH
Publication of EP1548280A1 publication Critical patent/EP1548280A1/fr
Application granted granted Critical
Publication of EP1548280B1 publication Critical patent/EP1548280B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • 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
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/12—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having plural sets of cylinders or pistons

Definitions

  • the invention relates to a reciprocating compressor, in particular for charging a Internal combustion engine is suitable.
  • the charging of internal combustion engines is not only a proven means for torque and Performance increase, but also to reduce consumption in part-load operation of a Internal combustion engine with predetermined maximum power.
  • the charge of diesel engines is particularly advantageous because in diesel engines existing in gasoline engines knocking problems not available.
  • the invention has for its object to provide a reciprocating compressor, which is at Simple design characterized by high efficiency and versatile.
  • a reciprocating compressor has a bilateral compressor End walls closed cylinder 2, in which a piston 4 is movable back and forth.
  • the Piston 4 includes two mutually spaced piston bottoms 6 and 8, the are advantageously equipped at their peripheral edges for sealing with piston rings and which separate two working chambers 10 and 12 inside the cylinder 2.
  • the two Piston bottoms 6 and 8 are connected by struts 14 rigidly together, for example screwed.
  • Guiding surfaces 16 and 17 are formed, which serve to guide sliding blocks 18.
  • the cylinder 2 is by means of brackets, which form partitions 28 and 30, in a housing 32nd added.
  • the housing 32 has at least one suction opening 34 and a Outlet opening 36, wherein, as can be seen, between the outer housing 32 and the Cylinder 2 formed gap is divided by the partitions 28 and 30 such that an inlet passage 38 is formed, which the suction port 34 with the inlet valves 20 and 22nd or of these optionally open or closed, in the working chambers 10 and 12, leading inlet ports connects, and an outlet channel 40 is formed, which the exhaust valves 24, 26 or of these optionally open or closed outlet openings of Working chambers 10 and 12 connects to the discharge opening 36.
  • FIG. 1 the direction of movement of the piston 4 is horizontal. In Figs. 2 to 8 it is perpendicular, so that the representations of Figs. 2 to 8 in accordance with the arrangement according to. FIG. 1 rotated by 90 °.
  • Figs. 2 and 3 show perspective views of the piston 4 with two of the pistons passing crankshafts 42 and 44.
  • the relative to the cylinder 2 and the housing 32nd stationary axes of the crankshaft are designated in Fig. 1 with A.
  • Each crankshaft points at least one each eccentrically to its axis arranged crank pulley 46 and 48, which with the sliding blocks 18 cooperates, along the guide surfaces 16, 17 of the piston heads.
  • 6 and 8 are linearly displaceable perpendicular to the axes of the crankshafts, so that a sliding block or slide guide is created, with the orbiting eccentric motion of the Crank disks in a conventional manner in an oscillating movement of the within Cylinder 2 guided piston can be converted.
  • the sliding blocks are advantageously divided for ease of assembly.
  • Fig. 4 shows the crankshafts 42 and 44 in an embodiment for each two within a Housing 32 (Fig. 1) arranged one behind the other cylinder 2, in each of which a piston. 4 is working.
  • each piston on the crankshaft 42 has two crank disks 46 and at the crankshaft 44, a crank disc 48 associated with the corresponding Sliding blocks 18 work together.
  • the crank disks 46 and 48 are axial offset from each other, so that their trajectories penetrate radially, creating a smaller distance between the crankshafts 42 and 44 is possible.
  • Balancing weights 50 and 52 are the crankshafts 42 and 44 in a conventional manner with Balancing weights 50 and 52 provided.
  • crankshafts 42 and 44 for example, in each case in the wall of the cylinder. 2 be stored.
  • the crankshaft cams 54 and 56 To drive the valves 20, 22, 24 and 26, the crankshaft cams 54 and 56, with which are actuated via actuators, the valves. So that only one of the external Crankshafts 42, 44 must be driven, is at one end of the crankshaft rotatably a gear 58 and 60 connected to the respective crankshaft.
  • the gears 58 and 60 are the same size and mesh with each other so that the crankshafts 42 and 44 are rotate in opposite directions at the same speed.
  • the gears 58, 60 serve as Elements of a gear pump, which in a coolant and / or lubricant circuit of the Compressor is arranged.
  • Fig. 5 shows the gem.
  • FIG. 6 shows a perspective view of sections of a left side of FIG Crankshafts 42, 44 arranged, a cylinder associated crank / valve train.
  • each crankshaft 42 and 44 on both sides outside of the cylinder Cam 54 and 56 formed with which roller tappet 62 and 64 work together, the each actuate a cylinder-like cross-over valve member 66 and 68, respectively.
  • the As shown in FIG. 6 left valve member 66 actuates a plurality of inlet valves 20 (Fig. 1).
  • the right Valve member 68 actuates a plurality of outlet valves 24.
  • the valves are on forcibly guided the respective valve members.
  • valve drives equal to each other or mirror symmetry arranged.
  • valve drive will be explained in more detail below with reference to FIGS. 9 to 13:
  • valve members 66 and 68 are linearly movable in housing-fixed guides, not shown guided and are of the cams 54 and 56 against the force of the springs 70 and 72, respectively supported between the housing 32 and the respective valve member, reciprocated.
  • the bridge-type valve member 66 which actuates the exhaust valves 20, contains for each Exhaust valve, a guide passage 74 through which the stem of the exhaust valve 20th extends through and which leads into a recess 76 in which the shaft of the valve ends. Between an end flange 78 of the valve stem and the valve member 66 is supported Valve spring 80 from which urges the exhaust valve 20 in the closed position. The end flange 28 opposite is screwed into the valve member 66, a grub screw 82, the Game setting serves.
  • the valve member 68 actuating the exhaust valves 24 ( Figure 10) also has one for each Exhaust valve 24 has a guide passage 84 through which the valve stem passes extends.
  • the valve stem 84 terminates in a stop 86 screwed to it, for example, whose distance from the valve plate to the game setting is adjustable.
  • a valve spring 88 Between the valve member 68th and the valve is supported by a valve spring 88.
  • roller tappet 62 with roller 88 mounted in it and fixed to the housing Leadership 90.
  • FIG. 13 shows a section of the two crankshafts 42 and 44 with the cams 54 and 56.
  • the crankshaft 42 has only one Crankshaft 46, whereas the crankshaft 44 has two crank disks 48.
  • the cam 54, the intake valves associated with the roller tappet or Bridge members 66 actuated, designed as a "negative cam", the bridge member 66th normally in the position gem.
  • Fig 9 against the springs 70 urges and only in his cam portion formed a smaller diameter as shown in FIG. 9 taking place Downward movement of the valve member 66 causes the opening of the inlet valve 20.
  • the the Cam associated with exhaust valves 56 of the crankshaft 44 is as a normal cam in the Diameter enlarged cam lobe formed.
  • the cylinder 2 are then mounted, each of two centrally subdivided halves. Subsequently, the valve trains are in each case on the cylinders mounted mounting surfaces mounted and the entire assembly is in the same assembled two-piece housing 32.
  • the cylinder halves and the Housing halves can be integrally formed with each other.
  • Fig. 14 shows a reciprocating compressor 92 according to the invention to the suction side of a Motor housing or cylinder head 94 of an internal combustion engine flanged.
  • 96 is one Pulley designated to drive one of the crankshafts.
  • Be flanged suction assembly for example, a throttle and / or a May include means for measuring the inflowing air amount, etc.
  • the compressor is operated in two-stroke operation.
  • the piston 4 1 moves from left to right, especially the inlet valve 20 and the Exhaust valve 26 is actuated such that fresh air flows into the working chamber 10 and from the Working chamber 20 compressed fresh air expelled at appropriate pressure level becomes.
  • the intake valve 22 and the exhaust valve 24 are moving from left to right the piston 4 advantageously to.
  • the operations of the valves are in opposite directions, i. the fresh charge flow is then determined by the inlet valve 22 and outlet valve 24, whereas where the valves 20 and 26 are preferred.
  • the reciprocating compressor according to the invention works, even if they only with a cylinder and arranged therein, a double-acting piston containing, with high efficiency and low pressure pulsations.
  • the formation of the piston with two at a mutual distance arranged piston crowns, between which the crank mechanism is arranged not only has the Advantage that the crankshaft and its lubrication is completely separate from the work spaces, but also allows easy storage of the crankshaft (s) in the cylinder wall.
  • the reciprocating compressor can be any number of cylinders with pistons working therein , wherein the individual cylinders are operated out of phase, so that minimal Pressure pulsations are achieved.
  • the possible small stroke / bore ratio allows low piston speeds, which favorably affects the fatigue life.
  • the design allows based on the cylinder cross-section large cross sections of the inlet and Outlet valves, whereby the compressor operates with low flow resistance.
  • the loader can on the pressure side directly on the cylinder head or a suction pipe of a be flanged onto the engine to be charged.
  • the housing 32 When flanging directly to the cylinder head can the housing 32 is connected along its length a plurality within the housing Have discharge ports 36 which lead directly into the inlet channels of the individual cylinders.
  • a suction can be flanged in front of the compressor, for example, a Throttle cap contains a connection for exhaust gas recirculation or from which a bypass line going out, bypassing the compressor directly into a suction pipe of the Internal combustion engine leads.
  • the design allows for a high surface-to-volume ratio in terms of the stroke volume, whereby large charge exchange valves are possible.
  • the crank mechanism may include one or more crankshafts, the implementation of the Rotary movement of the crankshaft (s) in a stroke movement of the piston on a variety of, on Known mechanisms can take place.
  • the mechanism described by means of sliding or Sliding blocks is easy to install, works smoothly and leads to a soft, sinusoidal movement of the pistons.
  • the described embodiment with two counter-rotating crankshafts can as Lancester compensation work, with oscillating, sinusoidal mass forces of piston and Sliding blocks in the crank mechanism of each piston are completely compensated.
  • crank pin or the crank disks with mutual axial offset leads on the one hand to a compact design and on the other hand, to a small mechanical stress and thus high speed stability of the crank mechanism.
  • the gears 58 and 60 at the ends of the crankshaft are used for synchronization and Power transmission between the crankshafts.
  • the gears can also through Belting, such as a toothed belt, to be replaced. It just needs a crankshaft of be driven one end, for example by means of the pulley 96 (Fig. 14).
  • the gears 58 and 60 may be used as elements of a gear pump, with which a cooling / lubricating fluid can be conveyed in the compressor or supercharger trained channels circulates.
  • a cooling / lubricating fluid can be conveyed in the compressor or supercharger trained channels circulates.
  • at least the working chamber 10 and 12 limiting walls of the cylinder cooled, with the short heat conduction paths for a provide efficient cooling.
  • the loader may additionally have a front of the discharge opening 36th having arranged internal heat exchanger. Alternatively or additionally, the compressed Air flow through an external heat exchanger before entering the internal combustion engine.
  • the advantageously integrally formed lubricant / coolant circuit of the supercharger can with the be connected to the internal combustion engine or be formed separately.
  • an important aspect of the compressor according to the invention is that on the one hand the compressed air flowing through the discharge opening 36 is free from any lubricant and on the other hand is as cool as possible.
  • the two crankshafts the are simultaneously camshafts, are passed between the piston plates and in the cylinder 2 are mounted by means of simple sealable bearings, so that within the piston one after each outside dense lubricant space is formed, the liquid lubricant, at the same time as Coolant is used, can be fed through the crankshaft.
  • the Lubricant / Coolant can effectively cool the piston crowns from the inside. It is understood that through through the cylinder wall, the space between the cylinder and the housing and the Housing passing channels a fluid return is formed, so that the coolant / lubricant circulates.
  • Shaft guides for the roller tappets 64 can wetting through the crankshafts be lubricated so that the lubricant does not get into the fresh air. Are advantageous very hard ram ends or contact surface combinations.
  • valves For the connection of the valves to valve lever or, as in the example shown, to the bridge-like valve members is a friction and wear-favorable material pairing advantageous.
  • the charger according to the invention advantageously operates in the two-stroke process.
  • the intake and exhaust valves can be operated in a variety of ways. in the Embodiment, they can not only with the appropriate dimensioning of the springs Valve members are actuated, but also work as check valves, the Inlet valves open at negative pressure in the respective working chamber and the exhaust valves at Open overpressure. In alternative embodiments, only the intake valves or only the Exhaust valves are designed as check valves and the other valves of the or Crankshafts be actuated.
  • the intake and / or exhaust valves may be by means known per se Valve actuation mechanisms, for example, by changing the effective tap lever and / or the Abgriffswinkel, are also controlled such that their opening or Locking function is variable, and / or can be held in the open or closed position.
  • the speed of the crankshaft of the compressor can be rigid with the crankshaft Internal combustion engine coupled. Between the supercharged internal combustion engine and the Compressor can be arranged a gearbox with stepwise or continuously adjustable ratio be. By means of a clutch, the compressor can be completely removed from the internal combustion engine be uncoupled.
  • the flow rate of the compressor can also be changed by variable control of the valves be in which, in open-position valves, a low-flow path of the Suction opening 34 to the discharge opening 36 (Fig. 1).
  • the delivery rate of the loader can be controlled by openings in the partitions 28 and 30th be changed as needed.
  • the inlet opening 34 may be preceded by a throttle valve be.
  • each of the crankshafts with two or three be provided more associated with each piston crank disks.
  • valves can also be completely independent of the rotation of the crankshaft by its own Drives, such as electromagnetic, hydraulic or other suitable actuators are actuated. Instead of the two crankshafts, only one crankshaft can pass through each piston extend, etc.
  • the compressor offers numerous possibilities for the regulation of maximum Compression of the air via light compression, no compression to the recoil, in which the compressor is used for braking.
  • the compressor or supercharger according to the invention is suitable for charging all types of Internal combustion engines, two-stroke engines, four-stroke engines or with other timing sequences working machines, gasoline engines, diesel engines, gas engines, etc.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Dry Shavers And Clippers (AREA)
EP04030336A 2003-12-23 2004-12-21 Compresseur à piston Active EP1548280B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10360920 2003-12-23
DE10360920A DE10360920B3 (de) 2003-12-23 2003-12-23 Hubkolbenverdichter

Publications (2)

Publication Number Publication Date
EP1548280A1 true EP1548280A1 (fr) 2005-06-29
EP1548280B1 EP1548280B1 (fr) 2006-10-11

Family

ID=34530377

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04030336A Active EP1548280B1 (fr) 2003-12-23 2004-12-21 Compresseur à piston

Country Status (6)

Country Link
US (1) US7780425B2 (fr)
EP (1) EP1548280B1 (fr)
JP (1) JP4491683B2 (fr)
CN (1) CN100424345C (fr)
AT (1) ATE342441T1 (fr)
DE (2) DE10360920B3 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005042004A1 (de) * 2005-09-05 2007-03-08 Mahle International Gmbh Verfahren zur Herstellung eines Verbrennungsmotors
WO2013159925A1 (fr) 2012-04-25 2013-10-31 Peter Kreuter Procédé permettant de faire fonctionner un moteur à combustion interne à turbocompresseur à gaz d'échappement

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8328538B2 (en) * 2007-07-11 2012-12-11 Gast Manufacturing, Inc., A Unit Of Idex Corporation Balanced dual rocking piston pumps
US7950357B2 (en) * 2007-12-21 2011-05-31 Meta Motoren-Und Energie-Technik Gmbh Method for operating an internal combustion engine and an internal combustion engine
DE102009018870B3 (de) * 2009-04-24 2010-11-18 Meta Motoren- Und Energietechnik Gmbh Hubkolbenverdichter mit Schieberventil
CN102889122B (zh) * 2011-07-21 2015-04-15 上海汽车集团股份有限公司 增压器
TWI463073B (zh) * 2011-12-22 2014-12-01 Fu Sheng Ind Co Ltd 多段式熱泵壓縮機
TWI509249B (zh) * 2013-11-06 2015-11-21 Electrnic Automatic Factory Tech 震動器及具有該震動器之電子元件測試分類機
DE102013112670A1 (de) * 2013-11-18 2015-05-21 Bitzer Kühlmaschinenbau Gmbh Kühlkreislauf
US20150322937A1 (en) * 2014-05-09 2015-11-12 Westinghouse Air Brake Technologies Corporation Oil-free compressor crankcase cooling arrangement
US11225111B2 (en) 2015-09-16 2022-01-18 Illinois Tool Works Inc. Tire pressure control system and components
DE102016100439A1 (de) * 2016-01-12 2017-07-13 GETAS GESELLSCHAFT FüR THERMODYNAMISCHE ANTRIEBSSYSTEME MBH Verfahren zum Betrieb eines Axialkolbenmotors sowie Axialkolbenmotor
KR101981097B1 (ko) * 2017-09-11 2019-05-22 엘지전자 주식회사 리니어 압축기
CN116906295B (zh) * 2023-08-15 2024-06-07 佛山市鼎聿精密科技有限公司 一种高效直线运动的双曲轴活塞结构、压缩机及真空泵

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US5219273A (en) * 1992-05-29 1993-06-15 General Motors Corporation Torsional damper for air conditioning compressor
WO2003087577A1 (fr) * 2002-04-18 2003-10-23 Kabushiki Kaisha Unicla J Compresseur du type a plaque oscillante

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Publication number Priority date Publication date Assignee Title
US4486157A (en) * 1981-12-16 1984-12-04 Nissan Motor Company, Limited Reciprocating compressor
US5219273A (en) * 1992-05-29 1993-06-15 General Motors Corporation Torsional damper for air conditioning compressor
WO2003087577A1 (fr) * 2002-04-18 2003-10-23 Kabushiki Kaisha Unicla J Compresseur du type a plaque oscillante

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005042004A1 (de) * 2005-09-05 2007-03-08 Mahle International Gmbh Verfahren zur Herstellung eines Verbrennungsmotors
WO2013159925A1 (fr) 2012-04-25 2013-10-31 Peter Kreuter Procédé permettant de faire fonctionner un moteur à combustion interne à turbocompresseur à gaz d'échappement
DE102012008107A1 (de) 2012-04-25 2013-10-31 Peter Kreuter Verfahren zum Betreiben einer abgasturboaufgeladenen Brennkraftmaschine sowie Brennkraftmaschine
DE102012008107B4 (de) * 2012-04-25 2014-08-07 Peter Kreuter Brennkraftmaschine mit Abgassammler und Zusatzverdichter sowie Verfahren zum Betreiben einer solchen Brennkraftmaschine

Also Published As

Publication number Publication date
JP2005180454A (ja) 2005-07-07
US20050152798A1 (en) 2005-07-14
ATE342441T1 (de) 2006-11-15
DE502004001717D1 (de) 2006-11-23
CN1637281A (zh) 2005-07-13
CN100424345C (zh) 2008-10-08
US7780425B2 (en) 2010-08-24
DE10360920B3 (de) 2005-09-22
JP4491683B2 (ja) 2010-06-30
EP1548280B1 (fr) 2006-10-11

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