EP2511531B1 - Compresseur à spirale pour fluide de refroidissement - Google Patents

Compresseur à spirale pour fluide de refroidissement Download PDF

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Publication number
EP2511531B1
EP2511531B1 EP12175341.2A EP12175341A EP2511531B1 EP 2511531 B1 EP2511531 B1 EP 2511531B1 EP 12175341 A EP12175341 A EP 12175341A EP 2511531 B1 EP2511531 B1 EP 2511531B1
Authority
EP
European Patent Office
Prior art keywords
outlet
valve
compressor
centre axis
valve seat
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 - Lifetime
Application number
EP12175341.2A
Other languages
German (de)
English (en)
Other versions
EP2511531A3 (fr
EP2511531A2 (fr
Inventor
Karl-Friedrich Kammhoff
Thomas Varga
Ruth Faber
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.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and Co KG
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 Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Publication of EP2511531A2 publication Critical patent/EP2511531A2/fr
Publication of EP2511531A3 publication Critical patent/EP2511531A3/fr
Application granted granted Critical
Publication of EP2511531B1 publication Critical patent/EP2511531B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/025—Lubrication; Lubricant separation using a lubricant pump
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S418/00—Rotary expansible chamber devices
    • Y10S418/01—Non-working fluid separation

Definitions

  • the invention relates to a compressor for refrigerants, comprising an outer casing, a arranged in the outer casing scroll compressor with a first, fixedly arranged in the outer casing compressor body and a second, relative to the first compressor body movable compressor body, each having a bottom and above the respective soil rising first or second spiral ribs, which mesh so that for compressing the refrigerant, the second compressor body relative to the first compressor body to form chambers on an orbital path about a central axis is movable, leading to a high pressure chamber in the outer housing outlet in the bottom of the stationary compressor body and a arranged between the outlet and the high-pressure chamber check valve with a valve body, which in an extending between a valve seat and a Hubflinder movement space freely between a through the Valvesi tz fixed closing position and a defined by the Hubfnatureer open position is movable.
  • Such a compressor with check valve is from the US 5,451,148 and also from the US 6,227,830 B1 known.
  • check valve In such a check valve is generally the requirement that this opens quickly, closes quickly and when opening as quickly as possible the largest possible cross-sectional area for a flow available.
  • the invention is therefore based on the object to improve a compressor of the type described above in such a way that the best possible function of the check valve is ensured.
  • the Hubflinder is provided with an opening which extends from a lying in the contact surface mouth opening a high-pressure side of the Hubfsseners extends. This ensures that the check valve closes quickly at a pressure drop in the scroll compressor, since even in the event that the valve body should stick to the Hubflinder, the valve body quickly dissolves the Hubflinder due to the pressurization of the breakthrough.
  • valve body can be released from the Hubflinder when the breakthrough is located laterally of the central axis of the movement space and thus the first acting on the valve body on the breakthrough force causes tilting of the valve body.
  • the aperture is arranged in an angular segment which lies on a side of the central axis of the movement space opposite the central axis of the outlet, so that the aperture lies in a semicircle about the central axis of the movement space, while the central axis of the outlet lies in the other semicircle.
  • the angular segment in which the aperture is located is symmetrical to a plane passing through the central axis of the outlet and the central axis of the movement space.
  • the angle segment could comprise a whole semicircle.
  • the angular segment within which the at least one breakthrough lies is approximately 150 °, more preferably approximately 120 °.
  • the object mentioned is achieved according to the invention in that the outlet has a central axis which is offset in relation to a central axis of the valve seat for the valve body in a transverse direction to the central axis.
  • This solution has the advantage that due to the staggered arrangement of the outlet relative to the valve seat, the valve experiences an asymmetrical force when opening due to the inflowing refrigerant and thus opens quickly.
  • the rapid opening of the valve body can be achieved if a cross-sectional area of a passage opening of the valve seat is greater than a cross-sectional area of the outlet, so that a relatively large force can be generated on the valve body by the refrigerant impinging on the valve body.
  • an antechamber having a larger cross-sectional area than the outlet is arranged between the valve seat and the outlet.
  • This prechamber expediently has a cross-sectional area which either corresponds to the cross-sectional area of the passage opening, which in turn should be larger than the cross-sectional area of the outlet, or larger than the cross-sectional area of the passage opening of the valve seat.
  • a central axis of the prechamber is arranged offset transversely to the central axis of the outlet.
  • the center axis of the pre-chamber substantially coincides with the central axis of the valve seat and thus both are arranged substantially coaxially with one another.
  • the movement space between the valve seat and the Hubflinder is preferably provided.
  • the movement space extends from the valve seat to the Hubflinder with an approximately the valve seat, that is in particular an outer diameter thereof, corresponding cross-sectional area in the direction of its central axis ,
  • valve bodies with a central plate-shaped part are known from the prior art, from which further arms extend or which is enclosed by openings.
  • valve body is plate-shaped with an approximately corresponding to the valve seat outer contour.
  • This solution has the advantage that no unnecessary the mass of the valve body enlarging additional arms or other elements are necessary to guide the valve body.
  • such a valve body can be optimally held and guided in the movement space defined above, whose cross-sectional area corresponds approximately to the cross-sectional area of the valve seat.
  • At least one outlet space is arranged laterally of the movement space, in particular radially outside thereof, which opens laterally into the movement space with an outlet opening between the lift catcher and the valve seat and leads to an outlet opening.
  • Such an outlet space makes it possible, when the valve body is lifted off the valve seat, in particular in the open position, to allow the refrigerant flow which propagates in the direction of the pressure arm to emerge with as large a cross section as possible and unhindered into the high pressure chamber.
  • a particularly large cross-section for the mouth opening of the outlet space in the movement space is available when the mouth opening of the outlet space extends to the valve seat, preferably between the Hubflinder and the valve seat.
  • the outlet opening of the outlet space could, for example, be arranged opposite the outlet opening.
  • a structurally expedient solution provides that the outlet opening is arranged in the region of the Hubfticianers.
  • the outlet opening is arranged so that it passes into a passage opening in the Hubfticianer and thus the exiting refrigerant flow through the outlet and the outlet opening also passes through the Hubftician.
  • a plurality of outlet spaces are arranged around the movement space.
  • an advantageous solution provides that the movement space is limited by at least one adjacent to the at least one mouth opening wall surface.
  • such a wall surface serves as a guide surface for the valve body, so that it is always held in the space provided for movement.
  • valve body is guided by a plurality of, for example, at the same angular distance about the central axis of the movement space arranged guide surfaces.
  • valve body is preferably provided with an end face which can be applied planar to the contact surface of the Hubfsseners.
  • the contact surface has a surface area which is greater than half the surface area of the end face.
  • the contact surface has a surface area which corresponds approximately to the surface area of the end face.
  • valve body is plate-shaped and the end face has a surface area which corresponds to more than half of an extension of the valve body transversely to its central axis.
  • the surface area of the end face is so large that it substantially corresponds to the cross-sectional area of the valve body.
  • the passage openings in the Hubflinder have so far made no detailed information.
  • the passage openings are in the Hubflinder outside of the movement space final part of the Hubflinders same.
  • FIG Fig. 1 to 5 An embodiment of a compressor according to the invention, shown in FIG Fig. 1 to 5 comprises an outer housing, designated as a whole by 10, in which is arranged a generally designated 12 spiral compressor, which can be driven by a drive unit designated as a whole by 14.
  • the scroll compressor 12 in this case comprises a first compressor body 16 and a second compressor body 18, wherein the first compressor body 16 has a same raised above a bottom 20, formed in the form of a Kreisvolvente spiral rib 22 and the second compressor body 18 a through a bottom 24 thereof elevating second, in the form of a Kreisvolvente trained spiral rib 26, wherein the spiral ribs 22, 26 engage each other and sealingly abut each of the bottom surfaces 28 and 30 of the other compressor body 18, 16, so that between the spiral ribs 22, 26 and form the bottom surfaces 28, 30 of the compressor body 16, 18 chambers 32, in which a compression of a refrigerant takes place, which flows over a spiral ribs 22, 26 radially surrounding the outside intake 34 with initial pressure and after the compression in the chambers 28 via an outlet 36 , provided in the bottom 20 of the first compressor body 16, emerges compressed to high pressure.
  • the first compressor body 16 is held firmly in the outer housing 10, by means of a separating body 40, which in turn is held on the outer housing 10 within the same, the bottom 20 of the first compressor body 16 overlaps at a distance and tight with a to the Outlet 36 around extending annular flange 42 of the first compressor body 16, which projects beyond the bottom 20 on one of the spiral rib 26 opposite side is connected.
  • a cooling chamber 44 for cooling the bottom 20 of the first compressor body 16 is formed, for example, the subject WO 02/052205 A2 is.
  • the second compressor body 18 is movable about a central axis 46 on an orbital path relative to the first compressor body 16, wherein the spiral ribs 22 and 26 theoretically abut one another along a contact line and the contact line also during the movement of the second compressor body 18 the orbital path revolves around the central axis 46.
  • the drive of the second compressor body 18 on the orbital path about the central axis 46 is effected by the already mentioned drive unit 14 which comprises an eccentric drive 50, a drive shaft 52 driving the eccentric drive 50, a drive motor 54 and a bearing unit 56 for supporting the drive shaft 52.
  • the eccentric drive 50 is formed by an eccentrically arranged on the drive shaft 52 and thus eccentrically to the central axis 46 driver 62 which engages in a fixedly connected to the bottom 24 of the second compressor body 18 driver receptacle 64, thus the second compressor body 18 on the orbital path to move about the central axis 46.
  • the bearing unit 56 in turn comprises a first bearing body 66, which represents a main bearing body and with a bearing portion 68, the drive shaft 52 supports in a region 70 and which carries the driver 62, wherein the driver 62 is preferably arranged integrally with the region 70.
  • the first bearing body 66 encloses a space 72 in which the eccentric drive 50 is arranged and in which a balancing mass 74 fixedly connected to the drive shaft 52 moves.
  • first bearing body 66 extends laterally of the space 72 in the direction of the bottom 24 of the second compressor body 18 and has around a second compressor body 18 facing opening 76 of the space 72 around extending wings 78, on which the second compressor body 18 with one of the second Spiral rib 26 opposite rear 80 rests and thus supported so that the second compressor body 18 is thereby secured against movement away from the first compressor body 16.
  • the fixation of the first bearing body 66 in the outer housing 10 is carried out with retaining arms 82 which extend radially from the first bearing body 66 to the outer housing 10 and hold in this the first bearing body 66 precise.
  • the first bearing body 66 further has on an opposite side of the holding arms 82 an outer surface 84 on which a within and spaced from a cylindrical portion 86 of the outer housing 10 extending, preferably also cylindrical housing sleeve 88 of a motor housing 90 sits, up to a second bearing body 92 forming a bottom of the motor housing 90, which is arranged at a distance from the first bearing body 66 and forms a bearing portion 94, in which the drive shaft 52 is mounted with an end portion 96 coaxial with the central axis 46.
  • the entire motor housing 90 thus extends within the cylindrical portion 86 of the outer housing 10 and at a distance therefrom.
  • the drive motor 54 is arranged between the first bearing body 66 and the second bearing body 92, which comprises a rotor 100 seated on the drive shaft 52 and a rotor 102 surrounding the stator 102, wherein the stator 102 of the housing sleeve 88 of the motor housing 90th is held stably fixed relative to the outer housing 10, so that a conventional gap 104 between the rotor 100 and the stator 102 is made.
  • stator 102 is provided on its housing sleeve 88 side facing with cooling channels 106 which extend parallel to the central axis 46, for example in the form of outer grooves in the stator 102 over the entire plant side 108, wherein the stator 102 via the plant side 108 at the housing sleeve 88 is supported.
  • a free space 112 is provided between the second bearing body 92 and a bottom part 110 of the outer housing 10, which opens up the possibility that in about the bottom part 110 with approximately vertically extending central axis 46 uplifting outer housing 10, an oil sump 114th forms, in which on the one hand lubricating oil accumulates due to gravity and on the other hand lubricating oil for lubricating the compressor according to the invention is kept ready.
  • the oil used for lubrication of the driver 62 in the driver seat 64 leaves the driver seat 64 in the region of an opening 132 facing the area 70 of the driver seat 64, then passes to a bottom 134 of the room 70 formed by the first bearing body 66 and from there via drain channels 136 Further, the oil used to lubricate the portion 70 of the drive shaft 52 in the bearing portion 68 exits therefrom on an underside 142 of the bearing portion 68, and thus, escapes from the bottom portion 134 of the motor housing 90 also in the upper interior 140 of the motor housing 90 a.
  • the suction port 152 a sleeve 154 which passes through the outer housing 10 of the compressor according to the invention and engages in a fixedly connected to the housing sleeve 88 of the motor housing 90 receptacle 156, as in Fig. 1 and 3 shown.
  • the receptacle 156 encloses an opening provided in the housing sleeve 88 inlet 158 for the refrigerant, so that it can enter directly into a lower interior 160 of the motor housing 90 which is located between the stator 102 and the second bearing body 92.
  • the inlet opening 158 is arranged in the direction of the central axis 46 so that the refrigerant at the level of a winding head 162 of the stator 102 enters the lower inner space 160, which also projects into the inner space 160.
  • a deflection unit 164 is associated with the inlet 158, which has two deflection surfaces 166 and 168 which redirect the refrigerant flowing approximately in the radial direction 170 to the central axis 46 through the sleeve 154, such that main flow directions of the supplied gaseous refrigerant in two opposite azimuthal directions 172 and 174 to the central axis 46 around the winding head 162 around within the housing sleeve 88, the inner wall 176 continues in the azimuthal directions 172 and 174 spreading refrigerant and helps that with the supplied refrigerant entrained oil is deposited on the inner wall 176 and at this in the direction of in Fig. 5 individually shown second bearing body 92 runs down.
  • bearing body 92 also forms the bottom 178 substantially closing the housing sleeve 88, which, however, is provided with oil discharge openings 180, from which the separating oil can flow into the oil sump 114.
  • the refrigerant entering the lower interior 160 of the motor housing 90 essentially does not have the possibility of transferring into the free space 112 between the second bearing body 92 and the bottom part 110, but essentially remains in the interior 160 for cooling the Winding head 162 and then passes, starting from the inner space 160 through the cooling channels 106 and the gap 104 between the rotor 100 and the stator 102 in the upper inner space 140 which lies between the first bearing body 66 and the stator 102 to those in the upper interior 140 projecting winding heads 182 to cool.
  • the gap 188 is located substantially between an inner wall surface 192 of the cylindrical portion 86 of the outer housing 10 and an outer wall surface 194 of the cylindrical housing sleeve 88, wherein the gap 188 preferably extends as a closed annular space around the housing sleeve 88 around.
  • the discharge opening 184 is opposite a deflection unit 200 arranged, which has deflection surfaces 202 and 204, which deflect the emerging from the outlet opening 184 gaseous refrigerant in the azimuthal directions 196 and 198.
  • the gaseous refrigerant in the azimuthal directions 196 and 198 in particular between the inner wall surface 192 and the outer wall surface 194 occurs due to the always acting radial acceleration of oil droplets in the gaseous refrigerant an oil separator, which is particularly in a precipitate of oil, the is carried by the refrigerant on the inner wall surface 192 and the outer wall surface 194, wherein the oil with the substantially vertical central axis 46 mounted compressor between the outer housing 10 and the motor housing 90 preferably along the inner wall surface 192 and the outer wall surface 194 run in the direction of the oil sump 114 can, as between the outer housing 10 and the motor housing 90 over the entire extent of the motor housing 90 in the direction of the central axis 46, starting from the gap 188 in the free space 112 overflowing free space 206 exists, via which the oil is ultimately fed to the oil sump 114.
  • the refrigerant thus substantially freed from oil in the oil separator 190 then flows, starting from the space 188 of the oil separator 190, between the holding arms 82 and thus outside the first bearing body 66 in the direction of the suction region 34 of the spiral compressor 12 and is sucked and compacted by the latter. wherein the compressed refrigerant enters through the outlet 36 and a subsequent check valve 208 in a high-pressure chamber 210 which is located between a cover 212 of the outer housing 10 and the separator body 40 and is discharged therefrom through a pressure port 214.
  • the check valve 208 has an antechamber 216 arranged following the outlet 36, and following this a valve seat 218, on which a valve body 220 can be placed.
  • a central axis 222 of the outlet 36 is offset laterally relative to a central axis 224 of the prechamber 216, so that the outlet 36 as a whole opens asymmetrically into the prechamber 216.
  • the pre-chamber 216 is provided with a cross-sectional area which is a multiple of the cross-sectional area of the outlet 36, so that the outlet 36 opens with the full cross-sectional area in a bottom 226 of the prechamber 216.
  • the pre-chamber 216 then extends below with its compared to the outlet 36 enlarged cross-sectional area to the valve seat 218 in the direction of the central axis 224, so that when lifted valve body 220 in the region of the valve seat 218, a passage opening 228 with a cross-sectional area of the pre-chamber 216 corresponding cross-sectional area for Flow through the valve seat 218 is available.
  • the valve body 220 is formed as a plate-shaped closed, that is formed without openings to an outer contour 238 extending body, wherein the outer contour 238 has a geometrically simple shape, such as a circle, but the shape can also be elliptical, rectangular, possibly formed with rounded corners be.
  • a movement space 230 for the valve body 220 rises above the valve seat 218 and has a central axis 232 which coincides with the central axis 224.
  • the movement space 230 extends along the central axis 232 above the valve seat 218 up to a hub catcher designated as a whole by 240 which delimits the movement space 230 on a side opposite the valve seat 218.
  • the cross-sectional area of the movement space 230 corresponds approximately to the cross-sectional area in the region of the valve seat 218, so that the valve body 220 in the movement space 230 is free between a closed position (FIG. Fig. 7 ), in which the valve body 220 rests on the valve seat 218, and in an open position (FIG. Fig. 10 ), in which the valve body 220 abuts the Hubflinder 240.
  • the movement space 230 follows the valve seat 218 parallel to the central axis 232 extending guide surfaces 242 which are formed in the simplest case by the movement space 230 delimiting wall surfaces and are arranged for example at equal angular intervals from each other, to guide the valve body 220 in the direction of the center axis 232 of the movement space 230 on its peripheral side 238, so that in particular it is ensured that the valve body 220 comes to rest with the necessary precision in the transition from the open position to the closed position on the valve seat 218.
  • outlet spaces 244 lead to the liftgate 240 facing outlet openings 248, which in turn pass into provided in the Hubftician 240 passages 250, wherein the passage openings 250 in the Hubfzaner 240 have a cross-sectional area which is greater than the cross-sectional area of the outlet openings 248 of the outlet spaces 244th in the open position of the valve body 220 by the valve seat 218 in the movement space 230 entering gaseous refrigerant has the ability to leave the movement space 230 via the orifices 246, to flow through the outlet 244 and from the outlet 244 via the outlet 248 and the passage 250 in Hub catcher 240 enter the high pressure chamber 210.
  • the flow cross sections of the outlet spaces 244 and the outlet openings 248 and the passage openings 250 in the Hubflinder are chosen so that the moving space 230 and the outlet chambers 244 flowing gaseous refrigerant can flow around the valve body 220 standing in the open position and thereby contributes to the valve body 220 to move when opening the check valve 208 in the direction of the open position in which the valve body 220, for example, the Hubftician 240 rests.
  • the valve body 220 in turn has an upper end face 252 facing the lift catcher 240, which extends preferably over the entire extent of the valve body 220 transversely to the central axis 232 to the outer contour 238 and in the case of the open position of the valve body 220 - as in Fig. 10 represented - abuts a contact surface 254 of Hubflinders 240, wherein the contact surface 254 has a surface area substantially corresponding to the surface extent of the end face 252, so that the end face 252 over the entire surface of the contact surface 254 of the Hubfsseners 244 can be applied, in particular to damage the valve body 220 to avoid a rapid transition from the closed position to the open position.
  • the Hubflinder 240 is provided with an opening 260 which extends from a mouth opening 246 located in the abutment surface 254 of the lift catcher 240 to a top side 264 of the lift catcher 240 facing the high pressure chamber 210, to apply a force present in the high pressure chamber 210 to a pressure drop in the movement space 230 to let the breakthrough 260 facing portion of the end face 252 act and when detaching the valve body 220 with the end face 252 of the contact surface 254 then finally by the pressure in the high pressure chamber 210 a force acting on the entire end face 252 to the valve body 220th as far as de To move open position in the direction of the closed position in the movement space 230, that a flowing over the outlet 244 in the direction of the outlet 36 gase
  • the opening 260 is not arranged symmetrically with respect to the center axis 232, but laterally offset therefrom on an opposite side of the center axis 232 to the central axis 222 of the outlet 36 and also within an angular range W about the center axis 232, which is symmetrical to a plane E, which passes through the central axis 232 of the movement space 230 and the central axis 222 of the outlet 36 therethrough.
  • valve body 220 when the end face 252 is detached from the contact surface 254, the valve body 220 receives a force application which is asymmetrical with respect to the center axis 232, which results in the valve body 220, with the partial region of the end face 252 near the aperture 260, moving faster from the contact surface 254 lifts than with the overlying the outlet 36 portions, and thus the valve body 220 performs a slight tilting movement, which promotes the total detachment of the end face 252 of the contact surface 254 and also faster the valve body 220 moves into the refrigerant flow 262 faster through the outlet 244 and the movement space 230 passes in the direction of the prechamber 216, so that this refrigerant flow 262 accelerates the valve body 220 in the direction of the valve seat 218 and thus moves into the closed position.
  • valve body 220 from the open position into the closed position can also be accelerated by the outlet 36 opening asymmetrically into the bottom 226 of the prechamber 216 and thus overall in the prechamber 216 as well as in the movement space 230 a to the central axis 232 asymmetric refrigerant flow 266 from the high-pressure chamber 210 in the direction of the outlet 36 forms, which additionally contributes to the valve body 220 after leaving the open position accelerated to move to the closed position.
  • the check valve 208 is realized in that the outlet 36 and substantially the prechamber 216 are still seated within the bottom 20 of the compressor body 16, while in the one piece the bottom 20 integrally formed annular flange 42 of the valve seat 216, the movement space 230 and the outlet spaces 244 are incorporated, and finally the Hubflinder 240 is in the form of a lid on the annular flange 42.
  • the Hubflinder 240 has not only the described function in the inventive solution, but extends radially to the central axis 232 still so far in the direction of engaging the annular flange 42 separating body 40 that the Hubfzaner 240 effective between the annular flange 42 and the separator 40 seal 270th engages, which lies in a ring flange 42 surrounding the groove 272 and a pressure-resistant connection between the annular flange 42 and the separator body 40 causes.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)

Claims (14)

  1. Compresseur pour agent réfrigérant, comprenant un carter extérieur (10), un compresseur de type hélicoïdal (12) disposé dans le carter extérieur (10) et comportant un premier corps de compresseur (16) disposé de manière fixe dans le carter extérieur (10) et un deuxième corps de compresseur (18) mobile par rapport au premier corps de compresseur (16), lesquels présentent un fond (20, 24) et des premières ou deuxièmes nervures hélicoïdales (22, 26) s'élevant au-dessus du fond respectif (20, 24), lesquelles nervures s'engrènent l'une dans l'autre de telle sorte que, pour compresser l'agent réfrigérant, le deuxième corps de compresseur (18) est mobile par rapport au premier corps de compresseur (16) sur une trajectoire orbitale autour d'un axe médian (46) en formant des chambres (28), un orifice de sortie (36) dans le fond (20) du corps de compresseur (16) fixe menant jusqu'à une chambre de haute pression (210) dans le carter extérieur (10), ainsi qu'un clapet antiretour (208) disposé entre l'orifice de sortie (36) et la chambre de haute pression (210) comprenant un corps de soupape (220), lequel peut se déplacer librement dans une chambre de déplacement (230) s'étendant entre un siège de soupape (218) et un limiteur de course (240), entre une position de fermeture fixée par le siège de soupape (218) et une position d'ouverture fixée par le limiteur de course (240),
    caractérisé en ce que le limiteur de course (240) est doté d'au moins une perforation (260) laquelle s'étend depuis une embouchure (262) située dans une face de butée (254) vers un côté haute pression (264) du limiteur de course (240) et en ce que la ou les perforations (260) se trouvent à côté d'un axe médian (232) de la chambre de déplacement (230).
  2. Compresseur selon la revendication 1, caractérisé en ce que la ou les perforations (260) sont disposées dans un segment d'angle (W) situé sur un côté de l'axe médian (232) de la chambre de déplacement (230) opposé à une axe médian (222) de l'orifice de sortie (36).
  3. Compresseur selon la revendication 2, caractérisé en ce que le segment angulaire (W) est symétrique à un plan (E) traversant l'axe médian (222) de l'orifice de sortie (36) et l'axe médian (232) de la chambre de déplacement (230).
  4. Compresseur selon la revendication 3, caractérisé en ce que le segment angulaire (W) mesure 150°.
  5. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'orifice de sortie (36) présente un axe médian (222) décalé par rapport à un axe médian (224) du siège de soupape (218) pour le corps de soupape (220), dans un sens transversal par rapport à l'axe médian (224).
  6. Compresseur selon la revendication 5, caractérisé en ce qu'une aire de section d'un orifice de passage (228) du siège de soupape (218) est plus grande qu'une aire de section de l'orifice de sortie (36), et en ce qu'en particulier une préchambre (216) ayant une aire de section plus grande que l'orifice de sortie (36) est disposée entre le siège de soupape (218) et l'orifice de sortie (36).
  7. Compresseur selon la revendication 6, caractérisé en ce qu'un axe médian (224) de la préchambre (216) est décalé transversalement par rapport à l'axe médian (222) de l'orifice de sortie (36) et en ce qu'en particulier l'axe médian (224) de la préchambre (216) coïncide essentiellement avec l'axe médian (224) du siège de soupape (218).
  8. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que la chambre de déplacement (230) s'étend, avec une aire de section correspondant approximativement au siège de soupape (218) en direction de son axe médian, depuis le siège de soupape (218) vers le limiteur de course (240).
  9. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que sur un côté de la chambre de déplacement (230) est aménagée au moins une chambre de sortie (244) laquelle débouche latéralement dans la chambre de déplacement (230) avec une embouchure (246) entre le limiteur de course (240) et le siège de soupape (218) et conduit vers un orifice de sortie (248).
  10. Compresseur selon la revendication 9, caractérisé en ce que l'embouchure (246) de la chambre de sortie (244) s'étend jusqu'au siège de soupape (218).
  11. Compresseur selon la revendication 9 ou 10, caractérisé en ce que l'orifice de sortie (248) est disposé au niveau du limiteur de course (240) et en ce qu'en particulier l'orifice de sortie (248) se transforme en orifice de passage (250) dans le limiteur de course (240).
  12. Compresseur selon l'une quelconque des revendications 9 à 11, caractérisé en ce que plusieurs chambres de sortie (244) sont disposées tout autour de la chambre de déplacement (230).
  13. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que le limiteur de course (240) présente une face de butée (254) pour le corps de soupape (220).
  14. Compresseur selon la revendication 13, caractérisé en ce que le corps de soupape (220) présente une face avant (252) pouvant venir buter sur toute la surface contre la face de butée (254) du limiteur de course (240).
EP12175341.2A 2002-10-15 2003-08-20 Compresseur à spirale pour fluide de refroidissement Expired - Lifetime EP2511531B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10248926A DE10248926B4 (de) 2002-10-15 2002-10-15 Kompressor
EP03808684.9A EP1563189B1 (fr) 2002-10-15 2003-08-20 Compresseur de type helicoidal pour agent refrigerant

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP03808684.9A Division-Into EP1563189B1 (fr) 2002-10-15 2003-08-20 Compresseur de type helicoidal pour agent refrigerant
EP03808684.9A Division EP1563189B1 (fr) 2002-10-15 2003-08-20 Compresseur de type helicoidal pour agent refrigerant

Publications (3)

Publication Number Publication Date
EP2511531A2 EP2511531A2 (fr) 2012-10-17
EP2511531A3 EP2511531A3 (fr) 2014-05-21
EP2511531B1 true EP2511531B1 (fr) 2018-03-07

Family

ID=32049492

Family Applications (3)

Application Number Title Priority Date Filing Date
EP12175341.2A Expired - Lifetime EP2511531B1 (fr) 2002-10-15 2003-08-20 Compresseur à spirale pour fluide de refroidissement
EP03808684.9A Expired - Lifetime EP1563189B1 (fr) 2002-10-15 2003-08-20 Compresseur de type helicoidal pour agent refrigerant
EP03022491A Expired - Lifetime EP1413758B1 (fr) 2002-10-15 2003-10-08 Compresseur à spirales avec séparateur d'huile

Family Applications After (2)

Application Number Title Priority Date Filing Date
EP03808684.9A Expired - Lifetime EP1563189B1 (fr) 2002-10-15 2003-08-20 Compresseur de type helicoidal pour agent refrigerant
EP03022491A Expired - Lifetime EP1413758B1 (fr) 2002-10-15 2003-10-08 Compresseur à spirales avec séparateur d'huile

Country Status (9)

Country Link
US (2) US6960070B2 (fr)
EP (3) EP2511531B1 (fr)
CN (3) CN1688817B (fr)
AT (1) ATE314578T1 (fr)
DE (2) DE10248926B4 (fr)
DK (1) DK1413758T3 (fr)
ES (1) ES2254846T3 (fr)
SI (1) SI1413758T1 (fr)
WO (1) WO2004036044A1 (fr)

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Also Published As

Publication number Publication date
DK1413758T3 (da) 2006-05-08
EP1563189B1 (fr) 2015-12-09
US20040126261A1 (en) 2004-07-01
CN1688817A (zh) 2005-10-26
SI1413758T1 (sl) 2006-06-30
EP1563189A1 (fr) 2005-08-17
EP1413758A2 (fr) 2004-04-28
ES2254846T3 (es) 2006-06-16
EP1413758B1 (fr) 2005-12-28
EP2511531A3 (fr) 2014-05-21
EP1413758A3 (fr) 2004-05-19
CN1497182A (zh) 2004-05-19
CN102116293A (zh) 2011-07-06
US7112046B2 (en) 2006-09-26
DE10248926A1 (de) 2004-05-06
CN1292171C (zh) 2006-12-27
DE50302045D1 (de) 2006-02-02
DE10248926B4 (de) 2004-11-11
US6960070B2 (en) 2005-11-01
CN102116293B (zh) 2013-05-01
CN1688817B (zh) 2012-06-27
ATE314578T1 (de) 2006-01-15
US20050232800A1 (en) 2005-10-20
EP2511531A2 (fr) 2012-10-17
WO2004036044A1 (fr) 2004-04-29

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