DE102016103315A1 - Compressor - Google Patents

Compressor

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Publication number
DE102016103315A1
DE102016103315A1 DE102016103315.4A DE102016103315A DE102016103315A1 DE 102016103315 A1 DE102016103315 A1 DE 102016103315A1 DE 102016103315 A DE102016103315 A DE 102016103315A DE 102016103315 A1 DE102016103315 A1 DE 102016103315A1
Authority
DE
Germany
Prior art keywords
compressor
pin
mass
body
characterized
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.)
Pending
Application number
DE102016103315.4A
Other languages
German (de)
Inventor
Dimitri Gossen
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
Priority to DE102016103315.4A priority Critical patent/DE102016103315A1/en
Publication of DE102016103315A1 publication Critical patent/DE102016103315A1/en
Application status is Pending legal-status Critical

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/32Correcting- or balancing-weights or equivalent means for balancing rotating bodies, e.g. vehicle wheels
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02Rotary-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
    • F04C18/0207Rotary-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
    • F04C18/0215Rotary-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00Combinations 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
    • F04C23/008Hermetic pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021Systems for the equilibration of forces acting on the pump
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00Components
    • F04C2240/60Shafts
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00Components
    • F04C2240/80Other components
    • F04C2240/807Balance weight, counterweight
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02Lubrication; Lubricant separation
    • F04C29/023Lubricant distribution through a hollow driving shaft

Abstract

A compressor comprising a compressor housing, a scroll compressor unit disposed in the compressor housing having a first compressor body and a second compressor body movable relative to the first compressor body, an axial guide supporting and supporting the movable compressor body against movements in a direction parallel to a center axis of the stationary compressor body Movements in the direction transverse to the central axis, an eccentric drive for the scroll compressor unit having a driven by the drive motor and on the orbital path around the central axis of a drive shaft revolving driver, which in turn cooperates with a cam receiver of the second compressor body, and a self-rotation of the second compressor body preventing clutch, to improve the smoothness, it is proposed that the eccentric drive driving a cam eccentric drive pin and mass balance szapfen and that the eccentric drive pin and the mass balancing body are arranged on opposite sides of a mass balance plane.

Description

  • The invention relates to a compressor comprising a compressor housing, a scroll compressor unit arranged in the compressor housing with a first, stationary compressor body and a second movable relative to the compressor body stationary compressor body whose formed in the form of a Kreisvolvente first and second spiral ribs mesh to form compressor chambers, When the second compressor body is moved relative to the first compressor body on an orbital track, an axial guide supporting the movable compressor body against movements in the direction parallel to a center axis of the stationary compressor body and moving in the direction transverse to the central axis, a drive motor which drives a Eccentric drive for the scroll compressor unit drives, one of the drive motor driven and circulating on the orbital path around the central axis of a drive shaft Mitn ehmer, which in turn cooperates with a cam receiver of the second compressor body, and a self-rotation of the second compressor body preventing coupling.
  • Such compressors are known from the prior art, in these there is the problem to achieve the greatest possible smoothness in operation.
  • The invention has the object to improve the smoothness in a compressor of the type described above.
  • This object is achieved according to the invention in a compressor of the type described above, that the eccentric drive has an eccentric drive pin driving the driver and a mass balancing body and that the eccentric drive pin and the mass balance pin are arranged on opposite sides of a mass balance plane.
  • The advantage of the solution according to the invention lies in the fact that the use of the mass balancing body creates the possibility of compensating in a simple manner the unbalance caused by the eccentric drive pin and in particular asymmetrical to the mass balance plane.
  • With regard to the course of the mass balancing level, no details were given in this context.
  • Thus, it is preferably provided that the mass balance plane passes through the central axis of the drive shaft and the central axis of the orbiting movable compressor body and thus these two central axes is exactly defined in their position and orientation.
  • In order to achieve the greatest possible smoothness, it is preferably provided that the mass balance body has a mass which deviates from the mass of the eccentric drive pin to a maximum of 20%, more preferably at most 10% in order to achieve the greatest possible compensation of the imbalance caused by the eccentric drive pin ,
  • It is particularly favorable when the mass balance body has substantially the same mass, in particular the same mass, as the eccentric drive pin.
  • In order to create the same conditions as possible with respect to the mass distribution as the eccentric drive pin, it is provided that the mass balance body is designed as a mass balance pin.
  • With regard to the arrangement of the journal axes of the mass balance pin and the eccentric drive pin, it is preferably provided that a pin axis of the mass balance pin is arranged at the same distance from the mass balance plane as an eccentric pin axis of the eccentric drive pin.
  • Furthermore, with regard to the orientation of the journal axes so far no further details have been made.
  • It is particularly favorable if the pin axis of the mass balance pin extends substantially parallel, preferably parallel to the eccentric pin axis of the eccentric pin.
  • Furthermore, it is particularly advantageous if the pin axis of the mass balance pin and the eccentric pin axis of the eccentric pin extend parallel to the mass balance plane.
  • In connection with the use of an eccentric drive spigot in the eccentric drive, it has not been specified in detail how the eccentric drive spigot should be arranged.
  • So it is particularly possible to arrange the eccentric pin either in the drive shaft or in the driver fixed and provide that it rotatably engages in a bearing bore in the driver or in the drive shaft.
  • A particularly preferred solution provides that the eccentric drive pin in the drive shaft is arranged tightly and engages in the provided in the driver bearing bore.
  • Furthermore, it is possible in the context of the inventive solution that the mass balancing pin is arranged either fixed in the drive shaft or in the driver and engages in a receiving this game with clearance in the driver or in the drive shaft.
  • Also in this solution is advantageously provided that the mass balance pin is fixed in the drive shaft and engages in the recess provided in the driver.
  • For example, while the recess is formed in the driver so that it allows at least limited rotation of the driver about the eccentric pin axis and relative to the mass balancing pin.
  • This can be done, for example, that the recess is large enough or designed as a cutout to allow the intended rotation of the driver relative to the Exzenterantriebszapfen.
  • In extreme cases, the recess is formed as such a large cutout of the driver that no contact of the driver takes place with the mass balance pin in the context of rotation provided.
  • The mass balance pin can be used particularly advantageously if it is an element of a movement limiting unit for the driver.
  • Such a movement limiting unit can be realized in particular advantageously if the recess forms a stop surface which limits a pivoting of the driver in the sense of reducing the compressor orbital radius by cooperation with the mass balancing pin.
  • In a structurally particularly easy to implement solution, it is preferably provided that the recess is arranged surrounding the mass balance pin with its inner wall surfaces and that a wall surface area thereof forms the stop surface.
  • In the simplest case, the recess can be designed as a bore which is chosen so large that a wall surface area of the inner wall surface of this bore comes into contact with the mass balance pin and thus forms the abutment surface.
  • It is preferably provided that in a normal state, in which the spiral ribs abut each other, the inner wall surface of the recess extends on all sides at a distance from the mass balance pin, so that no interaction between the recess and the mass balance pin occurs.
  • Only when leaving the normal state do the mass balancing pin and inner wall surface interact with the wall surface area forming the stop surface when the compressor orbital radius has been reduced from a normal state value to reach the minimum value which is definable by the relative location of the stop surface and the mass balance pin is.
  • In the context of the solution according to the invention, no detailed information on the total imbalance compensation was described.
  • Thus, an advantageous solution provides that the driver is provided with an orbital track compensation mass.
  • This orbital path compensation mass serves, in particular, to compensate for the imbalance which arises because the second movable compressor body moves on the orbital path.
  • In particular, it is provided that the Orbitalbahnausgleichsmasse is arranged symmetrically to the mass balance plane and thus does not cause unbalanced imbalance to the mass balance level.
  • A particularly favorable solution provides that the Orbitalbahnausgleichsmasse is disposed on a side opposite the Exzenterantriebszapfen and the mass balance pin side of a perpendicular to the mass balance plane and extending through the median plane of the drive shaft geometric transverse plane.
  • With regard to a further unbalance compensation, in particular the drive shaft, no further details were made in connection with the solutions described so far.
  • Thus, an advantageous solution provides that the drive shaft has a section facing the compressor, which cooperates with the eccentric drive pin and the mass balance body and carries a compressor-facing imbalance compensation mass
  • Preferably, it is provided that this imbalance compensation mass is arranged between a rotor of the drive motor and a front bearing unit on the drive shaft.
  • Furthermore, a favorable solution provides that the drive shaft has a compressor facing away portion, which carries a compressor imbalance unbalanced mass.
  • Also in this imbalance compensation mass is preferably provided that it is arranged between the rotor of the drive motor and a rear bearing unit of the drive shaft.
  • Preferably, it is also provided in these imbalance compensation masses, which are arranged on the drive shaft, that they are also formed and arranged symmetrically to the mass balance plane.
  • Further features and advantages of the invention are the subject of the following description and the drawings of some embodiments.
  • In the drawing show:
  • 1 a perspective view of a first embodiment of a compressor according to the invention;
  • 2 a longitudinal section through the first embodiment of the compressor according to the invention, in a running through a central axis of a stationary compressor body horizontal sectional plane;
  • 3 a longitudinal section through the first embodiment of the compressor similar 2 in a vertical cutting plane passing through the central axis of the stationary compressor body;
  • 4 a schematic representation of interdigitated spiral ribs and the orbiting movement of one of the spiral ribs and a representation of an orbital path of the movable spiral rib relative to the stationary spiral rib;
  • 5 a cross section through a scroll compressor unit along line 5-5 in 3 in the area of interlocking spiral ribs;
  • 6 a section along line 6-6 in 3 ;
  • 7 a section along line 7-7 in 3 ;
  • 8th an enlarged view of the area A in 7 ;
  • 9 a plan view of a drive shaft with a driven by this driver;
  • 10 a schematic geometric representation of the relative position of the center axes of the compressor body and an eccentric pin axis;
  • 11 a section through the driver with an orbital path compensation mass in the normal state value of the compressor orbital radius;
  • 12 similar to a cut 11 at a minimum value of the compressor orbit radius and
  • 13 a side view of a drive shaft with the driven by this driver.
  • An in 1 illustrated first embodiment of a whole as 10 designated compressor according to the invention for a gaseous medium, in particular a refrigerant, comprises as a whole with 12 designated compressor housing, which has a first end-side housing portion 14 a second end-side housing portion 16 and one between the end-side housing portions 14 and 16 arranged intermediate section 18 having.
  • As in 2 to 8th is shown in the first housing section 14 one as a whole with 22 designated spiral compressor unit is provided, which is a first in the compressor housing 12 , in particular in the first housing section 14 , Stationarily arranged compressor body 24 and a second relative to the stationary arranged compressor body 24 movable compressor body 26 having.
  • The first compressor body 24 includes a compressor body base 32 above which is a first spiral rib 34 elevates and the second compressor body 26 also includes a compressor body base 36 over which a second spiral rib 38 rises.
  • The compressor body 24 and 26 are arranged relative to each other so that the spiral ribs 34 . 38 interlock, as in 4 represented, between them at least one, preferably a plurality of compressor chambers 42 in which a compression of the gaseous medium, for example of refrigerant, takes place in that the second compressor body 26 himself with his central axis 46 around a central axis 44 of the first compressor body 24 on an orbital railway 48 moved with a compressor orbital trajectory VOR, wherein the volume of the compression chambers 42 and ultimately compressed gaseous medium through a central outlet 52 leaking while suckling gaseous medium through circumferentially opening compressor chambers 42 radially outboard relative to the central axis 44 is sucked.
  • The sealing of the compressor chambers 42 Relative to each other in particular also takes place in that the spiral ribs 34 . 38 frontally with axial sealing elements 54 respectively. 58 are provided on the respective floor surface 62 . 64 the other compressor body 26 . 24 lie sealingly, with the bottom surfaces 62 . 64 through the respective compressor body base 36 respectively. 32 be formed and in a direction perpendicular to the central axis 44 extending level lie.
  • The scroll compressor unit 22 as a whole is in a first housing body 72 of the compressor housing 12 taken, which has a front-side cover portion 74 and one on the frontal cover portion 74 integrally formed cylindrical ring section 76 which in turn has a ring attachment 78 in a sleeve body 82 of the housing body 72 engages the one at the intermediate section 18 forming central housing body 84 is formed, wherein the central housing body 84 on a first housing body 72 opposite side by a second housing body 86 is completed, the one inlet chamber 88 forms for the gaseous medium.
  • The sleeve body 82 encloses the scroll compressor unit 22 , whose first compressor body 24 to the compressor body base 32 molded support fingers 92 on a contact surface 94 in the housing body 72 supported.
  • In particular, the first compressor body 24 in the housing body 72 against all movements parallel to the support surface 94 immovably fixed.
  • This is the first compressor body 24 within the first housing body 72 and thus also inside the compressor housing 12 Fixed in a precisely defined position.
  • The second movable compressor body 26 who is on the orbital railway 48 around the central axis 44 relative to the first compressor body 24 must move, is relative to the central axis 44 in the axial direction by as a whole with 96 designated axial guide guided, which the compressor body base 36 at one of the spiral rib 38 opposite bottom 98 , in the area of an axial support surface 102 , supports and guides, allowing the compressor body base 36 the second compressor body 26 relative to stationary in the compressor housing 12 positioned first compressor body 24 and in the direction parallel to the central axis 44 is supported so that the Axialdichtelemente 58 on the floor surface 64 remain and not stand out from this, at the same time the compressor body base 36 with the axial support surface 102 transverse to the central axis 44 sliding relative to the axial guide 96 can move ( 2 . 3 and 6 ).
  • This is, as in the 2 . 3 and 7 shown, the axial guide 96 formed by a carrier element 112 , which is made in particular of an open-pore sintered material and the one of the Axialstützfläche 102 facing support surface 114 but not the compressor body base on which 36 with the axial support surface 102 but on which one as a whole with 116 designated in particular plate-shaped slider 116 with a sliding contact surface 118 rests, wherein the slider 116 with one of the sliding contact surface 118 opposite sliding support surface 122 the axial support surface 102 against movements parallel to the central axis 44 but supports sliding with respect to movements transverse to the central axis 44 supported leads.
  • This is an axial movement of the second compressor body 26 in the direction of the central axis 44 prevents movement in a plane transversely, in particular perpendicular, to the central axis 44 however possible.
  • The axial guide 96 according to the present invention provides that upon movement of the second compressor body 26 on the orbital railway 48 around the central axis 44 of the first compressor body 24 on the one hand, the second compressor body 26 with the compressor body base 36 and its axial support surface 102 relative to the slider 116 moves, on the other hand, the slider 116 in turn, relative to the support element 118 emotional.
  • Thus, there is sliding between the compressor body base 36 and the slider 116 by a movement of the axial support surface 102 relative to the sliding support surface 122 of the slider 116 instead of and also there is a sliding of the Gleitauflagefläche 118 of the slider 116 relative to the support surface 114 the carrier element 112 ,
  • To improve lubrication, for example, the Gleitstützfläche 122 and the sliding support surface 118 of the slider 116 provided with recesses, in particular micro-recesses, which form recordings for a lubricant and contribute to the distribution of the lubricant.
  • To the limited two-dimensional mobility of the slider 116 parallel to one to the central axis 44 vertical plane E relative to the carrier element 112 pretend is the slider 116 through an in 7 and 8th represented and as Whole with 132 designated guide with play relative to the support element 112 led, with the lead with game 132 one in the slider 116 provided guide recess 134 includes, which has a diameter DF, and one in the support element 112 anchored guide pin 136 whose diameter DS is smaller than the diameter DF, so that half of the difference DF-DS defines a guide orbital radius with which the slider 116 an orbiting movement relative to the carrier element 112 can perform.
  • Through the movements of the slider 116 a structure of sufficient lubricating film between the Axialstützfläche done 102 the compressor body base 36 and the sliding support surface 122 of the slider 116 as well as the support surface 114 and the Gleitauflagefläche 118 ,
  • For a stable lubricating film, it is sufficient if the guide orbital radius FOR is 0.01 times the compressor orbital radius or more, more preferably 0.05 times the compressor orbital radius or more.
  • Further, for example, due to the fact that the carrier element 112 at least in the area of the support surface 114 Made of an aluminum alloy, in addition, improved lubrication thereby ensuring that lubricant into the pores of the support element 112 occurs and thus on the example provided surface structures of the support element 112 in the area of the support surface 114 to build up the lubricating film in the gap is available.
  • Because of the slider 116 itself is designed as a plate-shaped, annular part made of spring steel and thus the support surface 114 facing Gleitauflagefläche 118 represents a smooth spring steel surface, the formation of the lubricating film is additionally promoted.
  • Furthermore, the material pairing of the aluminum alloy, in the region of the support surface 114 softer than spring steel, and the spring steel in the area of Gleitauflagefläche 118 due to the wear resistance advantageous endurance properties.
  • In the solution according to the invention, the carrier element 112 not only with the support surface 114 provided on which the sliding body 116 rests, but also with the bearing surfaces 94 on which the support fingers 92 of the first compressor body 24 support.
  • This gives the possibility of the position of the first compressor body 24 and the position of the second compressor body 26 in the direction of the central axis 44 relative to each other by suitable design of the support element 112 this particular by a single surface of the support element 112 which are both the support surface 114 as well as the bearing surfaces 94 includes, takes place.
  • Furthermore (as in 3 and 5 to 7 shown) the rotationally fixed fixing of the support fingers 92 relative to the carrier element 112 by both the carrier element 112 as well as the support fingers 92 penetrating positioning pins 142 ,
  • The carrier element 112 is also both axially in the direction of the central axis 44 as well as against rotational movements about the central axis 44 firmly seated in the housing body 72 arranged.
  • Furthermore, the structure of a lubricating film of lubricant between the Gleitstützfläche 122 and the axial support surface 102 ensure is the compressor body base 36 in a radially inner edge region 152 and in a radially outer edge region 154 with a relative to the axial support surface 102 inclined and opposite axial support surface 102 , reset running edge surface 156 respectively. 158 provided, which together with the Gleitauflagefläche 122 to a wedge-shaped radially outwardly or radially inwardly opening gap leads, which facilitates the access of lubricant.
  • Further, the structure of the lubricating film becomes between the sliding support surface 122 and the axial support surface 102 promoted by the fact that the Gleitstützfläche 122 and the axial support surface 102 , in which overlap region in which they cooperate as a continuous, that is in the circumferential direction U about the central axis and not interrupted in their entire radial extent annular surfaces 124 respectively. 126 are formed, in particular, the annular surface 126 the axial support surface 102 extends from an inner contour IK with a radius IR of the same starting up to an outer contour AK, wherein the radius IR is less than two-thirds of an outer radius AR.
  • Furthermore, the annular surface 124 the sliding support surface 122 dimensioned so that the ring surface 126 the axial support surface 102 in all relative movements to the sliding support surface 122 always on the entire surface rests on this.
  • As in the 2 to 7 represented, lie the Axialstützfläche 102 and the cooperating with this Gleitstützfläche 122 as well as the support surface 114 and the co-operating with this Gleitauflagefläche 118 all radially within a plurality of coupling element sets 162 having coupling 164 which are in equal radial Distances from the central axis 44 and at equal angular intervals in the circumferential direction U about the central axis 44 are arranged and together a clutch 164 forming a self-rotation of the second movable compressor body 26 prevented.
  • Each of these coupling element sets 162 includes, as in the 2 . 7 and 8th shown as the first coupling element 172 a pen body 174 , which has a cylindrical lateral surface 176 has and with this cylindrical lateral surface 176 in a second coupling element 182 intervenes.
  • The second coupling element 182 is through a ring body 184 formed, which has a cylindrical inner surface 186 and a cylindrical outer surface 188 has, which are arranged coaxially with each other.
  • This second coupling element 182 is in a third coupling element 192 guided, which as one in the support element 112 provided recording 194 for the ring body 184 is formed and which a cylindrical inner wall surface 196 having.
  • In this case, in particular, a diameter DI of the inner wall surface 196 larger than a diameter DRA of the cylindrical outer surface 188 of the ring body 184 and a diameter DRI of the cylindrical inner surface 186 necessarily smaller than the diameter DRA of the cylindrical outer surfaces 188 of the ring body 184 , In addition, wherein the diameter DRI the cylindrical inner surface 186 larger than a diameter DSK of the cylindrical lateral surface 176 of the pen body 174 ,
  • Thus, each coupling element set forms 162 in turn, an orbital guide whose maximum orbital radius OR for the orbiting motion DI / 2- (DRA-DRI) / 2-DSK / 2 corresponds.
  • By dimensioning the orbital radius OR of the coupling element sets 162 such that it is slightly larger than the compressor orbital trajectory VOR defined by the compressor bodies 24 and 26 the scroll compressor unit 22 , there is a guide of the movable compressor body 26 relative to the stationary compressor body 24 through the clutch 164 in such a way that, in each case one of the coupling element sets 162 is effective to the self-rotation of the second movable compressor body 26 to prevent, for example, six coupling element sets 162 after passing through an angular range of 60 ° the effectiveness of each coupling element set 162 from a coupling element set 162 for next in the direction of rotation coupling element set 162 replaced.
  • Due to the fact that each coupling element set 162 three coupling elements 172 . 182 and 192 and in particular a ring body 184 between the respective pen body 174 and the respective recording 194 is effective, on the one hand, the wear resistance of the coupling element sets 162 improves, on the other hand, the lubrication in the same area improved and beyond even the noise generated by the coupling element sets 162 reduced by changing the effectiveness of a coupling element set 162 to the other coupling element set 162 arises.
  • It is particularly essential that the coupling element sets 162 experience sufficient lubrication, in particular lubrication between the cylindrical surface 176 of the pen body 174 and the cylindrical inner surface 186 of the ring body 184 and a lubrication between the cylindrical outer surface 188 of the ring body 184 and the cylindrical inner wall surface 196 the recording 194 ,
  • For optimum lubrication of the coupling element sets 162 are the recordings 194 in the carrier element 112 open in the axial direction on both sides, wherein the annular body 184 through on their the second compressor body 26 opposite sides by a radially inwardly projecting stop element 198 are held.
  • In addition, in the carrier element 112 even more through holes 202 . 204 provided, which allow a passage of lubricant and sucked refrigerant.
  • To accommodate the pen body 174 trained coupling elements 172 is the compressor body base 36 with star-shaped projections extending radially outward 212 provided in intermediate spaces 214 between in a circumferential direction U about the central axis 44 successive support fingers 92 engage so that the coupling elements 172 also in these spaces 214 lie and thus within the housing body 72 in the largest possible radial distance from the central axis 44 are arranged.
  • This by the largest possible radial distance of the coupling elements 172 predetermined positioning of the coupling element sets 162 in as great as possible radial distance from the central axis 44 has the advantage that due to the large lever arm on the coupling element sets 162 acting forces can be kept as small as possible, which has an advantageous effect on the component dimensioning.
  • The inventive concept of lubrication of the axial guide 96 and the coupling element sets 162 is particularly advantageous if the central axes 44 and 46 the compressor body 24 and 26 Normally lying, that is maximally at an angle of 30 ° to a horizontal run, being in the compressor housing 12 , in particular in the region of the first housing body 72 at a lowest point in the direction of gravity a lubricant bath 210 forms from which swirled in the operation lubricant and thereby absorbed and distributed in the manner described.
  • The drive of the movable compressor body 24 takes place (as in 2 and 3 represented by) as a whole with 222 designated drive motor, for example, an electric motor, which in particular one in the central housing body 84 held stator 224 and one inside the stator 224 arranged rotor 226 which is on a drive shaft 228 is arranged, which is coaxial with the central axis 44 the stationary compressor body 24 runs.
  • The drive shaft 228 on the one hand in a between the drive motor 222 and the scroll compressor unit 22 and in the central housing body 84 arranged compressor facing storage unit 232 stored and on the other hand in a compressor facing away storage unit 234 on one of the storage unit 232 opposite side of the drive motor 222 is arranged.
  • The compressor-remote storage unit 234 is for example in the second housing body 86 stored, which the central housing body 84 on a first housing body 72 concludes opposite side.
  • From the second housing body 86 formed inlet chamber 88 while sucked medium, in particular the refrigerant flows through the drive motor 222 in the direction of the compressor facing storage unit 232 , flows around them and then flows in the direction of the scroll compressor unit 22 ,
  • The drive shaft 228 is pushing along as a whole 242 designated eccentric drive the movable compressor body 26 on, orbiting around the central axis 44 the stationary compressor body 24 emotional.
  • The eccentric drive 242 includes in particular one in the drive shaft 228 held eccentric drive pin 244 , which is a driver 246 on the orbital railway 48 around the central axis 44 moved, in turn, by a rotatable receiving the eccentric drive pin 244 in a bearing bore 247 in the driver 246 around an eccentric pin axis 245 rotatably on the eccentric pin 244 is stored and also around the central axis 46 the orbiting movable compressor body 26 rotatable in a pivot bearing 248 is stored, wherein the pivot bearing 248 a rotation of the driver 246 relative to the orbiting movable compressor body 26 allowed, as in 9 and 10 shown.
  • Due to the rotatability of the driver 246 around the eccentric pin axis 245 and around the central axis 46 is in particular the compressor orbital radius VOR, defined by the distance of the central axis 46 the movable compressor body 24 from the central axis 44 the stationary compressor body 24 and the drive shaft 228 , variably adjustable, so that the movable compressor body 26 each as far from the central axis 44 can move radially outward that the spiral ribs 34 . 38 abut each other and the compressor chambers 42 close tightly.
  • For this purpose, in particular the distance of the eccentric pin axis 245 from the central axis 44 the stationary compressor body 24 greater than the intended compressor orbital radius VOR, that is, the distance between the center axes 44 and 46 from each other, and so large that the eccentric pin axis 245 outside one through the two central axes 44 and 46 passing through the center axis ME and opposite to a direction of rotation D of the drive shaft 228 at a distance from this lies.
  • Due to this arrangement of the central axes 44 and 46 and the eccentric pin axis 245 causes the resulting eccentric action of the eccentric drive pin 244 on the driver 246 , a force FA, which relates to the central axis 46 of the driver 246 to one on the central axis 46 acting and the driver 246 together with the movable compressor body 26 radially to the central axis 44 outwardly moving force FC leads, passing through the central axis 44 and the central axis 46 extending median plane ME acts, and to which a tangential to the orbital path 48 Acting force FO leads the driver 246 together with the movable compressor body 26 on the orbital railway 48 around the central axis 44 emotional.
  • The through the central axes 44 and 46 defined center axis ME represents a plane of symmetry to a system formed by the mass of the drive shaft 228 and the mass of the movable compressor body 26 together with the mass of the driver 246 , and is also referred to as mass balance level ME.
  • The driver 246 is also in addition to mass balance with a one-sided held on this orbital balancing mass 252 Be provided with the imbalance by getting on the orbital railway 48 moving compressor body 26 counteracts and compensates as possible, including the Orbitalbahnausgleichsmasse 252 is formed and arranged symmetrically to the mass balance plane ME, as in 11 shown.
  • This is the Orbitalbahnausgleichsmasse 252 in particular on an eccentric drive pin 244 opposite side of a perpendicular to the mass balance plane ME and through the central axis 44 extending transverse plane QE.
  • The mass not taken into account in the mass balance described above is the mass of the eccentric drive pin 244 which is arranged asymmetrically to the mass balance plane ME and in particular at high rotational speeds of the drive shaft 228 leads to vibrations.
  • For this reason is in the drive shaft 228 in addition to the eccentric drive pin 244 another mass balancing pin 254 provided on a the eccentric drive pin 244 opposite side of the mass balance plane ME is arranged and thus with the eccentric drive pin 244 together again leads to an at least approximately symmetrical mass distribution to the mass balance plane ME.
  • Preferably, a pin axis 256 of the mass balance pin 254 and the eccentric pin axis 245 arranged mirror-symmetrically to the mass balance plane MR and also preferably have the eccentric drive pin 244 and the mass balancing pin 254 approximately the same mass.
  • To an inquire of the mass balance pin 254 in the driver 246 to enable is the driver 246 with a recess 258 provided the mass balance pin 254 with game absorbs, so that thereby a limited rotational movement of the driver 246 around the eccentric pin axis 255 to adjust the compressor orbital radius VOR to machining inaccuracies of the spiral ribs 34 . 38 or liquid shock or pressure surges is possible.
  • Preferably, as in 12 shown, the mass balance pin 254 with at least one surface area 262 an inner wall surface 264 the recess 258 a movement limiting unit 266 which, starting from a normal state, permits a reduction of the compressor orbital radius VOR from a normal state value only to a minimum value.
  • For further mass balance is the drive shaft 228 still with a compressor facing balancing mass 272 and a compressor imbalance compensation mass 274 Mistake ( 2 . 3 and 13 ).
  • The compressor-facing balancing mass 272 is preferably between the drive motor 222 and the compressor facing storage unit 232 on a compressor facing section 276 the drive shaft 228 it is located on the same side of the transverse plane QE as the orbital path compensation 252 and is arranged symmetrically to the mass balance plane ME.
  • The compressor-facing balancing mass 274 is preferably located on a compressor facing away section 278 the drive shaft 228 and between the drive motor 222 and the compressor remote storage unit 234 ,
  • For receiving the pivot bearing 248 is like in the 2 and 3 illustrated, the second compressor body 26 with an integrated cam receiver 282 provided, which is the pivot bearing 248 receives.
  • The driver intake 282 is relative to the flat side 98 the compressor body base 36 reset and thus in the compressor body base 36 integrated, so that the on the movable compressor body 26 acting driving forces on one of the spiral rib 38 facing side of the flat side 98 the compressor body base 36 are effective and thus with low tilting moment the movable compressor body 26 driving through the axial guide 96 in the direction of the central axis 44 seen between the driver intake 282 and the drive motor 222 at the axial support surface 102 axially supported and transverse to the central axis 44 is movably guided.
  • In the solution according to the invention is the Mitnehmeraufnahme 282 as in the 2 . 3 and 6 represented by the in the radial direction to the central axis 46 external Axialstützfläche 102 surrounded and the Axialstützfläche 102 is in turn from the radial direction to the central axis 44 external coupling element sets 162 the self-rotation of the second compressor body 26 preventing clutch 164 surround.

Claims (21)

  1. Compressor comprising a compressor housing ( 12 ), one in the compressor housing ( 12 ) arranged spiral compressor unit ( 22 ) with a first, stationary arranged compressor body ( 24 ) and a second, relative to the stationary arranged compressor body ( 24 ) movable compressor body ( 26 ), whose first and second spiral ribs (in the form of a circle involute) are ( 34 . 38 ) under Formation of compressor chambers ( 42 ) when the second compressor body ( 26 ) relative to the first compressor body ( 24 ) on an orbital path ( 48 ), an axial guide ( 96 ), which the movable compressor body ( 26 ) against movements in the direction parallel to a central axis ( 44 ) of the stationarily arranged compressor body ( 24 ) and when moving in the direction transverse to the central axis ( 44 ), an eccentric drive ( 242 ) for the scroll compressor unit ( 22 ), one of the drive motor ( 222 ) and on the orbital track ( 48 ) about the central axis ( 44 ) a drive shaft ( 228 ) rotating carrier ( 246 ), which in turn with a driver receptacle ( 282 ) of the second compressor body ( 26 ) and a self-rotation of the second compressor body ( 26 ) preventing coupling ( 164 ), characterized in that the eccentric drive ( 242 ) one the driver ( 246 ) driving eccentric drive pin ( 244 ) and a mass balance pin ( 254 ) and that the eccentric drive pin ( 244 ) and the mass balancing body ( 254 ) are disposed on opposite sides of a mass balance plane (ME).
  2. Compressor according to claim 1, characterized in that the mass balance plane (ME) through the central axis ( 44 ) of the drive shaft ( 228 ) and the central axis ( 46 ) of the orbiting movable compressor body ( 26 ) passes through.
  3. Compressor according to claim 1 or 2, characterized in that the mass balancing body ( 254 ) has a mass that is at most 20% of the mass of the eccentric drive pin ( 244 ) deviates.
  4. Compressor according to one of the preceding claims, characterized in that the mass balancing pin ( 254 ) substantially the same mass as the eccentric drive pin ( 244 ) having.
  5. Compressor according to one of the preceding claims, characterized in that the mass balance body as mass balance pin ( 254 ) is trained.
  6. Compressor according to claim 5, characterized in that a pin axis ( 256 ) of the mass balancing pin ( 254 ) is arranged at the same distance from the mass balance plane (ME) as an eccentric pin axis ( 245 ) of the eccentric drive pin ( 244 ).
  7. Compressor according to claim 5 or 6, characterized in that the pin axis ( 256 ) of the mass balancing pin ( 254 ) Substantially parallel to the eccentric pin axis ( 245 ) of the eccentric tapping pin ( 244 ) runs.
  8. Compressor according to one of claims 5 to 7, characterized in that a pin axis ( 256 ) of the mass balancing pin ( 254 ) and the eccentric pin axis ( 245 ) of the eccentric drive pin ( 244 ) runs parallel to the mass balance plane (ME).
  9. Compressor according to one of the preceding claims, characterized in that the eccentric drive pin ( 244 ) either in the drive shaft ( 228 ) or in the driver ( 246 ) is arranged tightly and in a bearing bore ( 267 ) in the driver ( 246 ) or in the drive shaft ( 228 ) rotatably engages.
  10. Compressor according to one of claims 5 to 9, characterized in that the mass balance pin ( 254 ) either in the drive shaft ( 228 ) or in the driver ( 246 ) is arranged tightly and in a game with this receiving recess ( 248 ) in the driver ( 246 ) or in the drive shaft ( 228 ) intervenes.
  11. Compressor according to one of claims 5 to 10, characterized in that the mass balance pin ( 254 ) an element of a movement limiting unit ( 264 ) for the driver ( 246 ).
  12. Compressor according to claim 11, characterized in that the recess ( 258 ) a stop surface ( 262 ), which pivoting of the driver ( 246 ) in the sense of reducing the compressor orbital radius (VOR) by interaction with the mass balance pin ( 254 ) limited.
  13. Compressor according to claim 12, characterized in that the recess ( 258 ) the mass balance pin ( 254 ) with their inner wall surfaces ( 264 ) and that a wall surface area thereof the stop surface ( 262 ).
  14. Compressor according to one of claims 10 to 12, characterized in that in a normal state in which the spiral ribs ( 34 . 38 ) abut each other, the inner wall surface ( 264 ) of the recess ( 258 ) on all sides at a distance from the mass balance pin ( 254 ) runs.
  15. Compressor according to one of the preceding claims, characterized in that the driver ( 246 ) with an orbital path compensation mass ( 252 ) is provided.
  16. Compressor according to claim 15, characterized in that the orbital track balancing mass ( 252 ) is arranged symmetrically to the mass balance plane (ME).
  17. Compressor according to claim 15 or 16, characterized in that the orbital track balancing mass ( 252 ) on an eccentric drive pin ( 244 ) and the mass balancing body ( 254 ) opposite side of a perpendicular to the mass balance plane (ME) and through the central axis ( 44 ) of the drive shaft ( 228 ) extending geometric transverse plane (QE) is arranged.
  18. Compressor according to one of the preceding claims, characterized in that the drive shaft ( 228 ) a compressor-facing section ( 276 ), which with the eccentric drive pin ( 244 ) and the mass balance body ( 254 ) and a compressor-facing imbalance compensation mass ( 272 ) wearing.
  19. Compressor according to claim 18, characterized in that the balancing mass ( 272 ) between a rotor ( 226 ) of the drive motor ( 222 ) and a front bearing unit ( 232 ) on the drive shaft ( 228 ) is arranged.
  20. Compressor according to one of the preceding claims, characterized in that the drive shaft ( 228 ) a compressor facing away section ( 278 ), which is a compressor imposing imbalance compensation mass ( 274 ) wearing.
  21. Compressor according to claim 20, characterized in that the balancing mass ( 274 ) between the rotor ( 226 ) of the drive motor ( 222 ) and a rear bearing unit ( 234 ) of the drive shaft ( 228 ) is arranged.
DE102016103315.4A 2016-02-25 2016-02-25 Compressor Pending DE102016103315A1 (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3519244A1 (en) * 1984-05-29 1985-12-05 Mitsubishi Electric Corp Hydraulic machine scroll type
DE3720745A1 (en) * 1986-06-23 1988-01-14 Hitachi Ltd Compressor scroll device
DE4305876A1 (en) * 1992-02-28 1993-09-02 Toyoda Automatic Loom Works Spiral compressor with anti-spin mechanism - uses counter mass with cylindrical depression to balance rotating spiral element
DE4336713A1 (en) * 1992-10-28 1994-05-05 Toyoda Automatic Loom Works Spiral compressor for vehicle air conditioning system - uses flanged screw and spring to control bush and weight on eccentric shaft
DE19953690A1 (en) * 1998-11-09 2000-06-08 Toyoda Automatic Loom Works Fuel cell system has movable spirals of compressor and regenerator symmetrically coupled to opposite ends of motor shaft

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3519244A1 (en) * 1984-05-29 1985-12-05 Mitsubishi Electric Corp Hydraulic machine scroll type
DE3720745A1 (en) * 1986-06-23 1988-01-14 Hitachi Ltd Compressor scroll device
DE4305876A1 (en) * 1992-02-28 1993-09-02 Toyoda Automatic Loom Works Spiral compressor with anti-spin mechanism - uses counter mass with cylindrical depression to balance rotating spiral element
DE4336713A1 (en) * 1992-10-28 1994-05-05 Toyoda Automatic Loom Works Spiral compressor for vehicle air conditioning system - uses flanged screw and spring to control bush and weight on eccentric shaft
DE19953690A1 (en) * 1998-11-09 2000-06-08 Toyoda Automatic Loom Works Fuel cell system has movable spirals of compressor and regenerator symmetrically coupled to opposite ends of motor shaft

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