EP2193274A1 - Machine à piston alternatif - Google Patents

Machine à piston alternatif

Info

Publication number
EP2193274A1
EP2193274A1 EP08785372A EP08785372A EP2193274A1 EP 2193274 A1 EP2193274 A1 EP 2193274A1 EP 08785372 A EP08785372 A EP 08785372A EP 08785372 A EP08785372 A EP 08785372A EP 2193274 A1 EP2193274 A1 EP 2193274A1
Authority
EP
European Patent Office
Prior art keywords
engine according
reciprocating piston
piston engine
reciprocating
radial shaft
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
EP08785372A
Other languages
German (de)
English (en)
Other versions
EP2193274B1 (fr
Inventor
Jan Hinrichs
Jens Dittmar
Tilo SCHÄFER
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.)
Magna Powertrain Bad Homburg GmbH
Original Assignee
Ixetic Mac 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 Ixetic Mac GmbH filed Critical Ixetic Mac GmbH
Publication of EP2193274A1 publication Critical patent/EP2193274A1/fr
Application granted granted Critical
Publication of EP2193274B1 publication Critical patent/EP2193274B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F04B27/08—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
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication

Definitions

  • the invention relates to a reciprocating engine according to the preamble of claim 1.
  • Reciprocating engines of the type discussed here are known. They are used in particular as a refrigerant compressor for regulating the passenger compartment temperature of a motor vehicle.
  • Such reciprocating engines comprise a pivoting element which has a variable pivot angle with respect to a plane on which the axis of rotation of a shaft of the reciprocating engine is perpendicular.
  • the pivoting element is pivotally connected to at least one driver element, via which the pivoting element also cooperates with the shaft, so that upon rotation of the shaft and the pivoting element rotates.
  • Such machines also have at least one parallel to the shaft arranged piston which is movably mounted in a bore of the cylinder block of the reciprocating engine.
  • the drive space is in communication with a refrigerant supply path and with a refrigerant return path.
  • the amount of refrigerant present in the drive chamber such as CO 2 in a CO 2 compressor, can be adjusted via the refrigerant supply path and via the refrigerant return path.
  • At least one radial shaft sealing ring is provided in the refrigerant return path, which cooperates with the shaft and preferably separates the refrigerant supply path from the refrigerant return path.
  • at least one screen and at least one throttle arranged in the refrigerant recirculation path. The screen absorbs any particles present in the refrigerant, which can otherwise cause clogging of the throttle.
  • the known reciprocating engines have the disadvantage that the radial shaft seal arranged in the refrigerant return path, the strainer and the throttle cause considerable assembly work.
  • Object of the present invention is therefore to provide a reciprocating engine, which is characterized by a particularly simple assembly days.
  • the reciprocating engine is characterized in that the radial shaft seal, the screen and the throttle form an assembly.
  • the radial shaft sealing ring, the sieve and the throttle are thus not spatially separated from each other in the reciprocating engine arranged, but quasi formed in the form of a module.
  • a reciprocating engine which is characterized in that the refrigerant return path is at least partially formed in the shaft of the reciprocating engine. Via an opening in the peripheral surface of the shaft, the refrigerant recirculation path is then in communication with the drive chamber, so that refrigerant which is present in the drive chamber via the refrigerant recirculation path can be removed.
  • the refrigerant supply path is at least partially formed in a cooperating with the shaft bearings.
  • the rolling bearing accommodating the shaft is advantageously lubricated by the oil-rich coolant, in particular a 01-CO 2 mixture.
  • the refrigerant supply path is in communication with the drive chamber via an opening in the rolling bearing.
  • Another preferred embodiment of the reciprocating engine is characterized in that the throttle and the radial shaft sealing ring are integrally formed.
  • the throttle and the radial shaft sealing ring are integrally formed.
  • a reciprocating engine in which the assembly consisting of the radial shaft seal, the screen and the throttle is arranged in a cylinder head of the reciprocating engine.
  • the assembly directly at one end of the shaft wherein the shaft is arranged at least partially in a recess in the cylinder head.
  • a reciprocating engine which is characterized in that the refrigerant supply path to the high pressure side of the reciprocating engine is in communication and thus oil-rich refrigerant, such as CO 2 , the drive chamber can be supplied.
  • the refrigerant return path is in communication with the suction region of the reciprocating piston engine, to which low-oil refrigerant in this way is supplied from the drive chamber.
  • a reciprocating engine which is characterized in that the assembly consisting of radial shaft seal, sieve and throttle, for example in a shaft receiving bore in the cylinder head of Hubkolbenmaschi- ne axially fixed by suitable means.
  • suitable means for example, a snap ring or a snapping lip contour, which is formed on the module, may be provided.
  • FIG. 1 shows a sectional illustration of a region of a reciprocating piston engine with a schematically represented assembly
  • Figure 2 is a sectional view of a portion of a reciprocating engine with an embodiment of an assembly
  • FIG. 3 is a sectional view of a detail of another exemplary embodiment of an assembly.
  • FIG. 1 shows a portion of a reciprocating engine 1 in a sectional view with a cylinder block 3 and a cylinder head 5.
  • a bore 7 is introduced, in which a piston, not shown here, is displaceable by means of a pivot member, also not shown.
  • valve assembly 8 which is provided at the right end of the present in the cylinder block 3 bore 7.
  • the valve assembly 8 allows for a movement of the piston, not shown here to the left in the bore 7, a suction of a refrigerant from a suction region, not shown and upon movement of the piston to the right in the bore 7 an ejection of the refrigerant in a high-pressure region, not shown the reciprocating engine 1.
  • the reciprocating piston engine 1 also has a shaft 9 which is driven, for example, via the belt drive of the engine of a motor vehicle and which rotates about a rotation axis M.
  • the shaft 9 is mounted in the cylinder block 3 by means of a bearing, here a rolling bearing 11 surrounding the shaft 9. Seen to the left of the roller bearing 11 is a shaft 9 surrounding the drive chamber 13, in which, inter alia, not shown here Swivel element is arranged. Furthermore, a certain amount of refrigerant, in particular CO 2 , is present in the drive chamber 13.
  • a refrigerant supply path 15 is provided in which refrigerant can pass through a bore 17 in the cylinder head 5 into a space 19 surrounding the shaft 9. Refrigerant present in the refrigerant supply path 15 then passes from the space 19 via an opening, not visible here, in the rolling bearing 11 into the drive chamber 13.
  • the preferably oil-rich refrigerant flowing through the rolling bearing 11 lubricates the rolling bearing 11 in an advantageous manner.
  • the refrigerant supply path 15 is connected to the high pressure side of the reciprocating piston engine 1, not shown here. It is therefore in the flowing into the bore 17 coolant in particular oil-rich coolant, such as an oil-CO 2 mixture.
  • Oil-rich refrigerant thus passes, as indicated by the arrow curve 21 in Figure 1, from the high-pressure region of the reciprocating piston engine 1 via the bore 17, the space 19 and the opening, not shown, in the rolling bearing 11 in the drive chamber 13, where it is the operating states of the reciprocating engine 1 influenced.
  • FIG. 1 makes it clear that a refrigerant return path 23 is also provided in the reciprocating piston engine 1.
  • the refrigerant recirculation path 23 first conveys refrigerant out of the drive chamber 13 via a bore 25, which is introduced into the shaft 9 at least in some areas, into a space 27 provided in the cylinder head 5. From there, the refrigerant finally reaches the cylinder via a linderkopf 5 existing bore 29 to the suction region of the reciprocating piston engine 1, not shown here.
  • a radial shaft seal 33 is provided, which is arranged in a bore 35 in the cylinder head 5 and the shaft 9 sealingly surrounds.
  • the radial shaft seal 33 separates the space 19 from the space 27, so that two separate refrigerant paths are present in the reciprocating engine 1.
  • a sieve 39 is provided which serves to trap present in the recycled refrigerant particles.
  • FIG. 1 makes it clear that the radial shaft sealing ring 33, the sieve 39 and the throttle 37 form an assembly or a module which is arranged in the area of the refrigerant return path 23.
  • the assembly formed from radial shaft seal 33, screen 39 and throttle 37 is arranged by way of example in the formed in the cylinder head 5 bore 35.
  • the radial shaft seal 33, the screen 39 and the throttle 37 for example, in the bore 35 of the cylinder head 5 as a unit or module, so that a complex separate assembly of the radial shaft seal 33, the strainer 39 and the throttle 37 is omitted in different areas of the cylinder head 5.
  • the assembly of these elements is thus considerably simplified by the training as an assembly.
  • Figure 2 shows a portion of a reciprocating engine in a sectional view with an embodiment of an assembly according to the invention, consisting of a radial shaft seal, a sieve and a throttle.
  • an assembly according to the invention consisting of a radial shaft seal, a sieve and a throttle.
  • the same parts are provided with the same reference numerals, so that reference is made to the description of Figure 1.
  • the exemplary embodiment according to FIG. 2 shows an assembly 41, in which the radial shaft sealing ring 33 shown in FIG. 1 and the throttle 37 are integrally formed as a component 43.
  • the screen 39 is surrounded by the component 43, or is embedded in this.
  • the assembly 41 is characterized particularly compact and can easily during assembly of the reciprocating engine 1, for example, in the bore 35 of the cylinder head 5, are used.
  • FIG. 2 makes it clear that the assembly 41 is arranged directly at one end of the shaft 9.
  • the assembly 41 is preferably fixed axially in the shaft 9 receiving bore 35 of the cylinder head 5, for example by means of a snap ring or formed on the assembly 41 flexible lip.
  • the component 43 has at its right end according to Figure 2, an opening 45 which allows a flow of refrigerant from the bore 25 in the shaft 9 to the here indicated only bore 29 in the cylinder head 5.
  • the opening 45 has a much smaller Diameter than the remaining area of the component 43 and thus acts as a throttle for the refrigerant flow.
  • a first sealing region 47 between the component 43 and the shaft 9 and a second sealing region 49 between the inner surface of the bore 35 and the component 43 separates the refrigerant return path, not shown here, from the refrigerant supply path, so that the component 43 also acts as a radial shaft sealing ring.
  • FIG. 3 shows a section of a further exemplary embodiment of the assembly 41.
  • the radial shaft sealing ring 33 and the throttle 37 are no longer combined in one piece into a component 43. Instead, a throttle 37 is inserted in a radial shaft seal 33.
  • the radial shaft sealing ring 33 is formed as an elastic part, for example made of an elastomer.
  • the throttle 37 is preferably made of a hard material, for example of metal, but in a particularly preferred manner of a hard plastic. The throttle 37 is connectable to the radial shaft seal 33. It can therefore simply be clamped in these, for example.
  • the throttle 37 can be glued into the radial shaft seal 33.
  • the throttle 37 has an opening 45 whose diameter is substantially smaller than the remaining areas of the assembly 41 and in particular the radial shaft seal 33rd
  • the radial shaft sealing ring 33 has a first sealing region 47, which can create elastic and sealing against the peripheral surface of a shaft 9. Dashed here is a first position of the first Sealing region 47 shown, which assumes this when no shaft 9 is in engagement with the radial shaft sealing ring 33. If, on the other hand, it is pushed onto a shaft 9, the first sealing region 47 is widened, resulting in an elastic restoring force which acts in a radial direction towards the central axis of the shaft 9. As a result, the first sealing region 47 is pressed sealingly against the surface of the shaft 9. This results in a very safe and dense system.
  • the radial shaft sealing ring 33 also has a second sealing region 49 which, as shown in FIG. 2, is intended to rest on the inner wall of a bore 35.
  • the second sealing region 49 has at least one projection 51 -in this case three projections 51-wherein preferably the diameter measured at the highest point of a projection 51 has an excess with respect to the inner diameter of the bore 35.
  • the screen 39 is held by a support ring 53.
  • This can be made of metal, plastic or another material. It is only essential that the screen 39 is embedded in the support ring 53 so that it is held securely by this.
  • the support ring 53 is clamped between the radial shaft seal 33 and the throttle 37, so that it is securely held in position by these elements. With a longer operating time and / or a high particle content in the carbon dioxide flowing through the sieve, contamination of the sieve can occur. This leads to a pressure build-up in front of the screen, whereby forces are introduced into this, which can cause buckling or loosening of the screen 39 and the support ring 53.
  • a stiffening frame 55 is embedded in the radial shaft sealing ring 33 of the exemplary embodiment shown here, which comprises a solid material, preferably consists of this.
  • the solid material may be metal or other suitable material.
  • the stiffening frame 55 has an angular or hook-shaped in cross section, which comprises a first leg 57 and a second leg 59.
  • the second leg 59 has a first region 59a, whose inner wall facing the sieve is aligned with an inner wall 61 of the radial shaft sealing ring 33.
  • a second region 59 b is further outwardly offset in the radial direction, so that it springs back from the inner wall 61.
  • The-seen in cross-section- angle or hook-shaped stiffening frame 55 introduces into the radial shaft sealing ring 33 radial biasing forces by which the support ring 53 with the sieve 39 and the throttle 37 are held securely. Even with an increased pressure, which can arise due to contamination of the sieve 39, deformation of the sieve 39 or of the support ring 53 can not occur, or the support ring 53 can not be pushed out of its predetermined clamping position. Likewise, the throttle 37 is held securely in its clamping seat due to the radial biasing forces.
  • the first leg 57 of the stiffening frame 55 causes increased axial stability of the assembly 41.
  • inventions of the assembly 41 shown in Figures 2 and 3 serve as purely exemplary embodiments. Also conceivable are other arrangements of the assembly 41, which summarize the three arranged in the refrigerant return path 23 elements radial shaft seal, sieve and throttle in an advantageous manner as compact as possible, so that they are preferably arranged in the same area of the refrigerant recycling path 23 in close proximity to each other.
  • the radial shaft sealing ring 33, the screen 39 and the throttle 37 form an assembly 41, in which the above-mentioned elements are not spatially separated, but preferably immediately adjacent to each other or are integrally formed.
  • the assembly 41 is particularly This is compact, so that a particularly simple installation is possible.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne une machine à piston alternatif (1), en particulier un compresseur frigorifique pour véhicules automobiles, cette machine comprenant un arbre (9) et une chambre d'entraînement qui est en liaison avec une voie de recyclage de réfrigérant dans laquelle sont disposés au moins un joint pour arbre tournant (47, 49), au moins un tamis (39) et au moins un élément d'étranglement (45), la chambre d'entraînement étant par ailleurs en liaison avec une voie d'amenée de réfrigérant (15) séparée de la voie de recyclage de réfrigérant. Le joint pour arbre tournant (47, 49), le tamis (39) et l'élément d'étranglement (45) forment un sous-ensemble (41).
EP08785372.7A 2007-08-25 2008-08-06 Machine à piston alternatif Not-in-force EP2193274B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007040227 2007-08-25
PCT/EP2008/006447 WO2009027009A1 (fr) 2007-08-25 2008-08-06 Machine à piston alternatif

Publications (2)

Publication Number Publication Date
EP2193274A1 true EP2193274A1 (fr) 2010-06-09
EP2193274B1 EP2193274B1 (fr) 2015-07-08

Family

ID=40032699

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08785372.7A Not-in-force EP2193274B1 (fr) 2007-08-25 2008-08-06 Machine à piston alternatif

Country Status (3)

Country Link
EP (1) EP2193274B1 (fr)
DE (1) DE112008002027A5 (fr)
WO (1) WO2009027009A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5413834B2 (ja) * 2009-11-27 2014-02-12 サンデン株式会社 往復動圧縮機
DE102014202511B4 (de) 2014-02-12 2015-12-03 Magna Powertrain Bad Homburg GmbH Hubkolbenmaschine
DE202015106322U1 (de) 2015-11-19 2017-02-22 BROSE SCHLIEßSYSTEME GMBH & CO. KG Kraftfahrzeugschloss

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1164289A3 (fr) * 2000-06-13 2003-09-24 Kabushiki Kaisha Toyota Jidoshokki Compresseur à plateau en biais

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2009027009A1 *

Also Published As

Publication number Publication date
EP2193274B1 (fr) 2015-07-08
WO2009027009A1 (fr) 2009-03-05
DE112008002027A5 (de) 2010-07-15

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