EP1662141B1 - Compresseur à pistons axiaux - Google Patents

Compresseur à pistons axiaux Download PDF

Info

Publication number
EP1662141B1
EP1662141B1 EP20050022276 EP05022276A EP1662141B1 EP 1662141 B1 EP1662141 B1 EP 1662141B1 EP 20050022276 EP20050022276 EP 20050022276 EP 05022276 A EP05022276 A EP 05022276A EP 1662141 B1 EP1662141 B1 EP 1662141B1
Authority
EP
European Patent Office
Prior art keywords
compressor
shaft seal
chamber
intake gas
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.)
Expired - Fee Related
Application number
EP20050022276
Other languages
German (de)
English (en)
Other versions
EP1662141A1 (fr
Inventor
Otfried Schwarzkopf
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.)
Valeo Compressor Europe GmbH
Original Assignee
Valeo Compressor Europe 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 Valeo Compressor Europe GmbH filed Critical Valeo Compressor Europe GmbH
Publication of EP1662141A1 publication Critical patent/EP1662141A1/fr
Application granted granted Critical
Publication of EP1662141B1 publication Critical patent/EP1662141B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/123—Fluid 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
    • 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
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • 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
    • 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
    • F04B27/1054—Actuating elements
    • F04B27/1063—Actuating-element bearing means or driving-axis bearing means
    • 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
    • F04B27/1081—Casings, housings
    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/125—Cylinder heads

Definitions

  • the invention relates to an axial piston compressor, in particular a compressor for the air conditioning system of a motor vehicle, according to the preamble of patent claim 1.
  • Such compressors are for example from the DE 196 47 861 , of the EP 0 688 953 , of the EP 0 838 590 , of the EP 0 911 517 , of the US 5,704,769 , as well as the US 5,733,107 known.
  • the above-cited references relate to compressors with a non-variable displacement, ie the tilt angle of the piston driving the swash plate is not changeable.
  • the compressor described in the cited documents often double or double-acting piston.
  • the engine as well as a surrounding engine compartment with respect to the axial extent are arranged centrally.
  • two cylinder blocks are usually connected on both sides, in each of which one end of the two piston ends of the piston is guided.
  • Usually are in these constructions usually three double-acting pistons.
  • valve plate assembly typically consists of a valve plate, suction valves, pressure valves and valve stoppers.
  • valve plate assembly in turn is followed by a cylinder head, which separates a suction chamber from a pressure gas chamber. Due to the explained compressor design cylinder block, valve plate assembly and the cylinder head are present in pairs.
  • the swash plate tilt angle is changed by varying the pressure in the engine compartment.
  • the pressure in the engine room can be varied to pressures between the high pressure level (i.e., the compression pressure) and the low pressure level (suction pressure).
  • the compressors according to the prior art are usually driven by a guided out of the compressor housing shaft end.
  • magnetic clutches and pulleys are used, via which the compressor with the engine speed can be driven.
  • the shaft seal regardless of which type it is, corresponds to the lower pressure level.
  • the impingement of the engine (despite any existing leaks) with the suction pressure is, as stated above, achieved by a short circuit between the engine chamber and suction chamber.
  • the cylinder head including the shaft seal includes, in concentric arrangement, a shaft seal chamber, as well as an annular suction chamber and an annular pressure chamber.
  • Such an arrangement is for example also from the EP 0 838 590 known while according to the DE 196 47 861 , of the EP 0 911 517 , of the US 5,704,769 and the US 5,733,107 , as well as the EP 0 688 953 a division of the cylinder head takes place in three chambers.
  • the shaft seals are usually arranged in the centrally located suction chamber.
  • the shaft seal is usually arranged in the axial extension on the cylinder head opposite side.
  • An arrangement of the shaft seal, in particular a mechanical Axialgleitringdichtung in the cylinder head or in the suction chamber has the advantage that the shaft seal on the one hand comparatively well by the suction gas in the suction chamber can be cooled and on the other hand by the lowest pressure within the compressor is applied (as for compressors with uncontrolled stroke is the case).
  • a disadvantage of the objects of EP 1 164 289 , of the EP 1 233 180 , of the EP 1 239 154 as well as the DE 102 06 748 is that the oil supply to the shaft seal is not optimally solved in operation, the refrigerant can be comparatively little cooling effect that the shaft seal, in particular the sealing gap, are in a kind of dead space (poor oil circulation) and that at compressor standstill no oil reservoir on the sealing rings can be present (oil flows away from the sealing gap), which inevitably leads to leaks in long downtimes.
  • a compressor according to the invention comprises a housing, a cylinder block, at least one in the cylinder block axially reciprocating piston and a cylinder head.
  • a suction chamber is disposed substantially in the cylinder head and the compressor further includes a suction gas inlet and a drive shaft.
  • An essential point of a compressor according to the invention is that the drive shaft between the suction chamber and the Sauggaseintritt is sealed to the outside, through a shaft seal. This ensures that the oil supply to the shaft seal is also optimized for longer downtime and in the operation of the compressor, since the oil can not flow out of the chamber (internal sealing element or oil level protection), while the suction gas cooling of the shaft seal also reaches an optimum level.
  • the shaft seal is arranged within a separate shaft sealing chamber, whereby an assembly-and maintenance-friendly (eg when mounting the shaft seal from the outside) axial piston is formed.
  • the shaft sealing chamber is preferably arranged between the suction chamber and the Sauggaseintritt, which ensures a constructively low cost.
  • an annular space is defined between the peripheral wall of the shaft sealing chamber and at least part of the shaft seal arranged therein, into which opening the suction gas inlet opens.
  • the annulus communicates preferably with an axial gap between the end face of the shaft seal and the end wall facing the side wall of the shaft seal chamber.
  • the width of the annular space and / or the axial gap is approximately between 1.5 mm and 5.0 mm.
  • the above-mentioned embodiments represent structurally simple variants of a compressor according to the invention, wherein the fact that the mean diameter of the shaft seal chamber is not significantly greater than the mean diameter of the shaft seal itself, the advantage that the entrained in the refrigerant flow oil or the In the refrigerant flow entrained oil tends to be larger than a relatively large shaft seal chamber. Furthermore, the flow rate of the refrigerant is comparatively larger and the cooling effect by turbulence and the corresponding forced convection greater than in a compressor with a larger shaft seal chamber.
  • the cylinder head is formed in one piece, which ensures a low production cost.
  • An alternative embodiment is characterized in that the cylinder head is made in two parts.
  • the components of the cylinder head may consist of the same materials, for example aluminum, or of different materials, for example of aluminum and steel.
  • Components containing large cavities can be constructed of a solid material (this is particularly advantageous for the use of CO 2 as a refrigerant), while the component that incorporates the shaft seal is made of a material that has good thermal conductivity. is trained.
  • a possible material for this is aluminum, which is distinguished not only by its good thermal conductivity but also by its low weight. This ensures sufficient heat dissipation to the environment.
  • a rotatably connected to the drive shaft pulley preferably has flow elements which cause a rotation of the same an air flow, which are directed to the cylinder head and the shaft seal receiving component of the compressor, so for example the shaft seal chamber.
  • the pulley is arranged on the side of the compressor facing the suction chamber. In addition to its functionality with respect to the drive of the compressor according to the invention, the pulley thus assumes a second function, namely to cool the compressor accordingly. As a result, optimal heat dissipation is achieved with low structural means.
  • the shaft sealing chamber is designed such that when a standstill of the compressor, an oil reservoir is held in the same.
  • the oil reservoir preferably reaches at least the lower edge of a sealing gap of the shaft seal.
  • the suction gas inlet leading into the shaft sealing chamber and the suction gas outlet leading out therefrom (toward the suction chamber) are arranged with respect to the installation position of the compressor so that they are by no means located on the underside of the shaft seal chamber or arranged so that complete emptying of the chamber is made possible, for example in compressor standstill.
  • all openings and recesses of the shaft sealing chamber in particular the openings for the connections between the shaft sealing chamber and the Sauggaseintritt or the shaft seal chamber and the suction chamber above the lower edge of the sealing gap of the shaft seal.
  • the opening in the shaft sealing chamber for the connection between the shaft sealing chamber and Sauggaseintritt is arranged such that it lies between the lower edge and the upper edge of the sealing gap. This ensures efficient cooling.
  • the opening for the connection between the shaft sealing chamber and suction gas inlet is located centrally between the lower edge and the upper edge of the sealing gap.
  • the openings for the connections between the shaft seal chamber and the suction gas inlet or the shaft seal chamber and the suction chamber are also arranged at a different level in the shaft seal chamber. Also, the arrangement at different heights, the cooling function is improved.
  • a further preferred embodiment of a compressor according to the invention promotes an optimal cooling function for the compressor:
  • the suction duct is formed such that from this emerging suction gas or the entire of this emerging suction gas flows mainly to the region of the sealing gap of the shaft seal and / or order the shaft seal is turned around. Such a construction further avoids a kind of "dead space" in terms of cooling.
  • the shaft seal in a compressor according to the invention should not only be cooled substantially by the suction gas and the entrained oil, but also by a heat dissipation to the outside, i. So a heat dissipation to the environment, which can be done directly or indirectly via the housing parts.
  • the cylinder head is formed at least in two parts, wherein between at least two components of said cylinder head, a thermal insulation is arranged so that in the shaft seal a comparatively cool component, in particular of a thermally highly conductive material such as aluminum is made.
  • the thermal insulation preferably comprises a steel sheet which is disposed on one or both sides, i. that is, elastomer-coated on a cylinder block facing side of the steel sheet and / or on a side facing away from the cylinder block of the steel sheet.
  • the shaft seal comprises a lip seal or an axial mechanical seal. This ensures a structurally easily executable embodiment of a compressor according to the invention. Furthermore, in a further preferred embodiment, cooling fins are arranged on the cylinder head, which ensure good heat dissipation.
  • a check valve is preferably arranged in or at the connection between the suction gas inlet and the shaft sealing chamber.
  • the preferred embodiment of the compressor 1 a housing 2, a cylinder block 3 and a cylinder head 4.
  • seven pistons (not shown) are mounted axially reciprocable.
  • a suction chamber 5 is arranged substantially in the cylinder head 4 and is in communication with a suction gas inlet 6.
  • the compressor is driven via a pulley 12 by means of a drive shaft 7.
  • the present compressor is a variable piston type compressor, the piston stroke being controlled by a pressure difference existing between the suction gas side and an engine chamber 7a.
  • a swiveling or swash plate 7b is deflected or pivoted more or less out of its vertical position. The larger the resulting swing angle, the larger the piston stroke, and accordingly, the higher the pressure at the outlet side of the compressor (DP) is provided.
  • a sealing of the drive shaft to the outside by a shaft seal 8, said shaft seal 8 between the suction chamber 5 and the Sauggaseintritt 6 is disposed within a separate shaft seal chamber 9.
  • the shaft sealing chamber 9 is arranged in its entire dimensions between the suction chamber 5 and the suction gas inlet 6. Between a peripheral wall of the shaft sealing chamber 9 and the shaft seal 8 arranged therein, an annular space 10 is delimited, into which the suction gas inlet 6 opens.
  • the annular space 10 is provided with an axial gap 11 which is arranged between an end face of the shaft seal 8 and the side wall of the shaft seal chamber 9 facing this end face.
  • the width of the annular space 10 and the axial gap 11 is approximately 3.0 mm, it being noted at this point that a width of about 1.5 mm and 5.0 mm can affect the flow conditions in the compressor low.
  • the cylinder head 4 of the present preferred embodiment is formed in two parts and is composed of two components 4a and 4b and an insulation 16 together. This ensures that parts which are subjected to a high load or are subjected to high pressure, made of a correspondingly tough material (steel) are made (part 4b), while parts which are subject to lower loads (part 4a), but for are optimized for heat dissipation, are made of a lighter, thermally highly conductive material (aluminum).
  • the two parts are separated by the thermal insulation 16.
  • This consists of a steel sheet which has a thickness of approximately 0.3 mm and is elastomer coated on both sides. Of course, steel sheets are conceivable, which are elastomer-coated on one side only.
  • the two sides are meant, which face the cylinder block 3 and the cylinder block 3 are facing away.
  • the component 4a accommodating the shaft seal 8 is made of aluminum because of the required good heat dissipation, while the member 4b accommodating the suction chamber 5 and especially the compressed gas outlet (DP) is made of steel.
  • the drive shaft 7 is rotatably connected to the pulley 12, wherein the pulley 12 is disposed on the side of the compressor 1 facing the suction chamber 5.
  • the pulley has flow elements 31 which, when rotated, impinge on the cylinder head 4, i.
  • the component 4a of the cylinder head which comprises the shaft seal, directed air flow (indicated by the arrows 32a and 32b) effect.
  • the shaft sealing chamber 9 is formed such that when a standstill of the compressor 1, an oil reservoir 14 is held in the shaft seal chamber 9 (see Fig. 2 ). From the schematic representation in Fig. 2 It can also be seen that in a connection 33 between the suction gas inlet 6 and the shaft sealing chamber 9, a check valve 15 is arranged. The connection between the shaft sealing chamber 9 and the suction chamber 5 is identified by the reference numeral 34.
  • a sealing lip 17 is arranged on the drive shaft 7, which seals the engine chamber against the pressurized components of the compressor.
  • a bearing 35 (see also Fig. 3 (b) ) are arranged.
  • the oil reservoir in the shaft seal chamber 9 exceeds, as shown Fig. 2 combined with Fig. 4 (especially Fig. 4 (a) ) is visible, a lower edge 36 of a sealing gap of the shaft seal 8.
  • Fig. 4 especially Fig. 4 (a)
  • the seal geometry consists of a ring 38 connected to the cylinder head 4 and a ring 39 which rotates with the shaft and is biased by a spring. From the detailed drawing of the chamber 9 in Fig. 4 are the lower edge 36 of the sealing gap as well as the Upper edge 37 of the sealing gap visible.
  • connection 33 and 34 are shown, wherein the connection 33 as already mentioned above is the one between the shaft seal chamber 9 and suction gas inlet 6, and the connection 34 is that between the shaft seal chamber 9 and the suction chamber 5.
  • the openings in the shaft sealing chamber 9 for the connections 33 and 34 are arranged above the lower edge 36 of the sealing gap of the shaft seal 8.
  • the opening for the connection 33 is arranged such that it lies centrally between the lower edge 36 and upper edge 37 of the sealing gap.
  • the openings for the connections 33 and 34, which are arranged in the shaft seal chamber 9 are arranged at a different level in the shaft seal chamber 9 (cf. Fig. 4 (a) ).
  • the suction gas channel 13 is further designed such that the suction gas, which emerges from the suction gas channel, on the one hand flows against the region of the sealing gap of the shaft seal 8 and on the other hand is deflected around the shaft seal 8. This ensures ideal flow conditions.
  • 4 cooling fins 30 are arranged on the cylinder head.

Landscapes

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

Claims (22)

  1. Compresseur à piston axial (1) avec un boîtier (2), un bloc-cylindres (3), au moins un piston se déplaçant axialement par un mouvement alternatif dans le bloc-cylindres (3), une tête de cylindre (4), une chambre de gaz pauvre (5) disposée essentiellement dans la tête de cylindre (4), qui est reliée à une entrée de gaz pauvre (6) dans le compresseur et avec un arbre de transmission (7),
    caractérisé en ce que
    l'arbre de transmission (7) entre la chambre de gaz pauvre (5) et l'entrée de gaz pauvre (6) est étanchéifié vers l'extérieur par un dispositif d'étanchéité d'arbre (8), le dispositif d'étanchéité d'arbre (8) étant disposé à l'intérieur d'une chambre de dispositif d'étanchéité d'arbre séparée (9) et sachant qu'entre la paroi périphérique de la chambre du dispositif d'étanchéité de l'arbre (9) et au moins une partie du dispositif d'étanchéité de l'arbre (8) agencé dedans, un espace annulaire (10) est délimité, dans lequel débouche l'entrée du gaz pauvre (6).
  2. Compresseur (1) selon la revendication 1,
    caractérisé en ce que
    la chambre du dispositif d'étanchéité de l'arbre (9) est agencée entre la chambre de gaz pauvre (5) et l'entrée de gaz pauvre (6).
  3. Compresseur (1) selon les revendications 1 ou 2,
    caractérisé en ce que
    la chambre du dispositif d'étanchéité de l'arbre de transmission (9) et la chambre de gaz pauvre (5) sont agencées dans l'extension axiale de l'axe longitudinal du compresseur, l'une derrière l'autre ou rangées l'une contre l'autre.
  4. Compresseur (1) selon l'une des revendications précédentes,
    caractérisé en ce
    qu'un ou l'espace annulaire (10) communique avec une fente axiale (11) entre une face avant du dispositif d'étanchéité de l'arbre (8) et la paroi latérale de la chambre du dispositif d'étanchéité de l'arbre (9) orientée vers cette face avant.
  5. Compresseur (1) selon les revendications 3 ou 4,
    caractérisé en ce que
    la largeur de l'espace annulaire (10) et /ou de la fente axiale (11) est d'environ 1,5 mm à 5,0 mm.
  6. Compresseur (1) selon l'une des revendications précédentes,
    caractérisé en ce que
    la tête de cylindre (4) a une configuration monobloc.
  7. Compresseur (1) selon l'une des revendications 1 à 5,
    caractérisé en ce que
    la tête de cylindre (4) est configurée en plusieurs parties, notamment en deux parties.
  8. Compresseur (1) selon la revendication 7,
    caractérisé en ce que
    le composant qui entoure ou reçoit le dispositif d'étanchéité de l'arbre (8) est configuré dans un matériau, qui présente une bonne conductibilité thermique, notamment en aluminium.
  9. Compresseur (1) selon l'une des revendications précédentes,
    caractérisé par
    une poulie (12) reliée à l'arbre de transmission (7) de manière à résister à la torsion, qui est agencée sur le côté du compresseur (1) orienté vers la chambre de gaz pauvre (5) et comporte des éléments fluidiques (31) qui provoque lors de la rotation de la poulie (12) un courant d'air (32a, 32b) dirigé sur la tête de cylindre (4) et le composant du compresseur (1) recevant le dispositif d'étanchéité de l'arbre (8).
  10. Compresseur (1) selon l'une des revendications précédentes,
    caractérisé en ce que
    la chambre du dispositif d'étanchéité de l'arbre (9) est configurée de telle manière qu'en cas d'arrêt du compresseur (1) un florentin (14) est maintenu dans la chambre du dispositif d'étanchéité de l'arbre (9).
  11. Compresseur (1) selon la revendication 10,
    caractérisé en ce que
    la chambre du dispositif d'étanchéité de l'arbre (9) comporte, pour maintenir le florentin (14), une paroi étanche à l'huile et/ou une garniture en labyrinthe et/ou une lèvre d'étanchéité (17).
  12. Compresseur (1) selon les revendications 10 ou 11,
    caractérisé en ce que
    le florentin (14) atteint au moins le bord inférieur (36) d'une fente étanche du dispositif d'étanchéité de l'arbre (8).
  13. Compresseur (1) selon l'une des revendications précédentes, notamment la revendication 12,
    caractérisé en ce que
    toutes les ouvertures et tous les évidements de la chambre du dispositif d'étanchéité d'arbre (9), notamment les ouvertures pour les liaisons (33, 34) entre chambre de dispositif d'étanchéité d'arbre (9) et entrée de gaz pauvre (6) ou chambre de dispositif d'étanchéité d'arbre (9) et chambre de gaz pauvre (6) sont agencés au-dessus du bord inférieur (36) de la ou d'une fente étanche du dispositif d'étanchéité de l'arbre (8).
  14. Compresseur (1) selon l'une des revendications précédentes,
    caractérisé en ce que
    l'ouverture pour la liaison (33) entre chambre du dispositif d'étanchéité d'arbre (9) et entrée de gaz pauvre (6) est agencée dans la chambre du dispositif d'étanchéité d'arbre de telle manière qu'elle se trouve entre bord inférieur (36) et bord supérieur (37) de la fente étanche.
  15. Compresseur (1) selon la revendication 14,
    caractérisé en ce que
    l'ouverture pour la liaison (33) se trouve au milieu, entre bord inférieur (36) et bord supérieur (37) de la fente étanche.
  16. Compresseur (1) selon l'une des revendications précédentes,
    caractérisé en ce que
    les ouvertures pour les liaisons (33, 34) entre chambre du dispositif d'étanchéité d'arbre (9) et entrée de gaz pauvre (6) ou chambre du dispositif d'étanchéité d'arbre (9) et chambre de gaz pauvre (5) sont agencées sur un niveau différent dans la chambre du dispositif d'étanchéité d'arbre (9).
  17. Compresseur (1) selon l'une des revendications précédentes,
    caractérisé en ce que
    le canal de gaz pauvre (13) est configuré de telle manière que le gaz pauvre sortant de celui-ci souffle principalement sur la ou une zone de la ou d'une fente étanche du dispositif d'étanchéité d'arbre (8) et/ou est articulé autour du dispositif d'étanchéité d'arbre (8) .
  18. Compresseur (1) selon l'une des revendications 7 à 17,
    caractérisé en ce
    qu'une isolation thermique (16) est disposée entre au moins deux composants de la tête de cylindre (4)0
  19. Compresseur (1) selon la revendication 18,
    caractérisé en ce que
    l'isolation thermique (16) comprend une tôle d'acier revêtue d'élastomère sur un côté ou sur les deux côtés, c'est-à-dire sur un côté orienté vers le bloc-cylindres (3) et/ou sur un côté opposé au bloc-cylindres (3).
  20. Compresseur (1) selon l'une des revendications précédentes,
    caractérisé en ce que
    le dispositif d'étanchéité d'arbre (8) comprend une garniture étanche à lèvre ou une garniture étanche à anneau glissant axial.
  21. Compresseur (1) selon l'une des revendications précédentes,
    caractérisé en ce que
    des ailettes de refroidissement (30) sont disposées sur la tête de cylindre (4).
  22. Compresseur (1) selon l'une des revendications précédentes,
    caractérisé en ce
    qu'un clapet anti-retour (15) est disposé dans ou sur la liaison (33) entre l'entrée de gaz pauvre (6) et la chambre du dispositif d'étanchéité d'arbre (9).
EP20050022276 2004-11-27 2005-10-12 Compresseur à pistons axiaux Expired - Fee Related EP1662141B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200410057367 DE102004057367A1 (de) 2004-11-27 2004-11-27 Axialkolbenverdichter

Publications (2)

Publication Number Publication Date
EP1662141A1 EP1662141A1 (fr) 2006-05-31
EP1662141B1 true EP1662141B1 (fr) 2008-10-08

Family

ID=35976676

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20050022276 Expired - Fee Related EP1662141B1 (fr) 2004-11-27 2005-10-12 Compresseur à pistons axiaux

Country Status (2)

Country Link
EP (1) EP1662141B1 (fr)
DE (2) DE102004057367A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11293554B2 (en) 2017-03-09 2022-04-05 Johnson Controls Technology Company Back to back bearing sealing systems

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2971821B1 (fr) * 2011-02-22 2013-08-23 Valeo Thermal Sys Japan Co Dispositif de lubrification d'un roulement secondaire dans un compresseur electrique
DE102019202905A1 (de) * 2019-03-04 2020-04-16 Vitesco Technologies GmbH Kältemittelverdichteranordnung, Verfahren zum Betreiben einer Kältemittelverdichteranordnung und Kraftfahrzeug

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4229145A (en) * 1977-01-27 1980-10-21 Diesel Kiki Co., Ltd. Swash plate compressor
JPS599757B2 (ja) * 1977-10-12 1984-03-05 株式会社日立製作所 圧縮機
JPH037581Y2 (fr) * 1986-06-13 1991-02-25
JP2609292B2 (ja) * 1988-06-22 1997-05-14 株式会社日立製作所 Ｇｐｓ測位装置
US5495789A (en) * 1993-03-10 1996-03-05 Sanden Corporation Swash plate type compressor with lubricating mechanism between the shoe and swash plate
JPH08261147A (ja) * 1995-03-20 1996-10-08 Toyota Autom Loom Works Ltd 往復動ピストン型圧縮機
JPH0960591A (ja) * 1995-08-21 1997-03-04 Toyota Autom Loom Works Ltd 圧縮機のオイル分離機構
JPH09144651A (ja) * 1995-11-20 1997-06-03 Toyota Autom Loom Works Ltd 往復動型圧縮機
KR100312933B1 (ko) * 1996-05-08 2002-05-13 이시카와 타다시 왕복운동형압축기
DE69825951T2 (de) * 1997-10-24 2005-09-15 Kabushiki Kaisha Toyota Jidoshokki, Kariya Taumelscheibenkompressor
EP1164289A3 (fr) * 2000-06-13 2003-09-24 Kabushiki Kaisha Toyota Jidoshokki Compresseur à plateau en biais
JP2002243000A (ja) * 2001-02-19 2002-08-28 Harmonic Drive Syst Ind Co Ltd 波動歯車減速機を備えたアクチュエータ
JP2002242839A (ja) * 2001-02-19 2002-08-28 Toyota Industries Corp 圧縮機
JP2002257043A (ja) * 2001-03-06 2002-09-11 Toyota Industries Corp 圧縮機
JP2003028057A (ja) * 2001-07-13 2003-01-29 Toyota Industries Corp 可変容量型圧縮機における絞り構造

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11293554B2 (en) 2017-03-09 2022-04-05 Johnson Controls Technology Company Back to back bearing sealing systems

Also Published As

Publication number Publication date
DE502005005604D1 (de) 2008-11-20
DE102004057367A1 (de) 2006-06-01
EP1662141A1 (fr) 2006-05-31

Similar Documents

Publication Publication Date Title
DE3545581C2 (fr)
DE4229069C2 (de) Taumelscheiben-Kältemittelkompressor für ein Kühlsystem
EP2333336B1 (fr) Machine à pistons pour l'utilisation comme pompe à vide à des fins médicales
DE4333144C2 (de) Kältemittelkompressor mit hin- und herbeweglichen Kolben
DE69104093T2 (de) Klimaanlagekompressor.
DE2544685A1 (de) Schmiersystem fuer kompressoreinheit
DE4401836C2 (de) Axialkolbenkompressor mit mehreren Kolben
DE3142230A1 (de) Mehrzylinder-kompressor
DE4333634A1 (de) Axialkolbenkompressor mit mehreren Kolben und einem Drehventil
DE19527675C2 (de) Kältemittelkompressor mit einfach wirkenden Kolben und Dämpfungseinrichtungen für Schwankungen des Anlaßdruckes
WO2013167124A2 (fr) Unité cylindre-piston
DE102007004187B4 (de) Regelbare Kühlmittelpumpe
DE4411437C2 (de) Axialkolbenkompressor mit Drehventil
DE19603109C2 (de) Kolben-Kältemittelkompressor mit verbesserter Dichtfunktion
EP1662141B1 (fr) Compresseur à pistons axiaux
DE3788176T2 (de) Schiefscheibenverdichter mit veränderlicher Verdrängung.
DE102016203587A1 (de) Taumelscheibenverdichter mit veränderlicher Verdrängung
DE102012104163B3 (de) Kolben-Zylinder-Einheit
DE3826548C2 (de) Flügelzellenverdichter mit variabler Förderleistung
DE10255680B4 (de) Axialkolbenverdichter, insbesondere CO 2-Verdichter für Fahrzeug-Klimaanlagen mit geteiltem Zylinderkopf
DE19614186C2 (de) Taumelscheibenverdichter
DE4326366A1 (de) Kompressor der Taumelscheibenbauart
DE2263837A1 (de) Radialkolbenpumpe
EP1725771B1 (fr) Compresseur, en particulier compresseur a pistons axiaux pour une installation de climatisation de vehicule
DE102005033707A1 (de) Vereinfachte, innenbeaufschlagte Axialgleitringdichtung für die CO2-Anwendung

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

17P Request for examination filed

Effective date: 20060630

17Q First examination report despatched

Effective date: 20060727

AKX Designation fees paid

Designated state(s): DE FR GB

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 502005005604

Country of ref document: DE

Date of ref document: 20081120

Kind code of ref document: P

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20090709

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20090831

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20081231

Year of fee payment: 4

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20091012

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20101230

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120501

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502005005604

Country of ref document: DE

Effective date: 20120501

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20091031