WO2018189041A1 - Système de compresseur à vis, à engrenage de synchronisation et à engrenage de transmission - Google Patents

Système de compresseur à vis, à engrenage de synchronisation et à engrenage de transmission Download PDF

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Publication number
WO2018189041A1
WO2018189041A1 PCT/EP2018/058813 EP2018058813W WO2018189041A1 WO 2018189041 A1 WO2018189041 A1 WO 2018189041A1 EP 2018058813 W EP2018058813 W EP 2018058813W WO 2018189041 A1 WO2018189041 A1 WO 2018189041A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
shaft
gear
screw compressor
arrangement
Prior art date
Application number
PCT/EP2018/058813
Other languages
German (de)
English (en)
Inventor
Ronald Sachs
Wolfgang Asal
Wolfgang Gorzawski
Original Assignee
Gardner Denver Schopfheim 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 Gardner Denver Schopfheim Gmbh filed Critical Gardner Denver Schopfheim Gmbh
Publication of WO2018189041A1 publication Critical patent/WO2018189041A1/fr

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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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/02—Arrangements for drive of co-operating members, e.g. for rotary piston and casing of toothed-gearing 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/04—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for reversible 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/001—Pumps for particular liquids
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/04—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for reversible machines or 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F04C2240/601—Shaft flexion
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/12—Vibration

Definitions

  • the invention relates to a screw compressor arrangement, in particular for the discharge of dry bulk materials, such as powder, granules, pellets, foodstuffs, in particular animal fats, or the like, from silo vehicles.
  • Screw compressor assemblies are well known in the art through prior public use. These have proven themselves in practice.
  • the invention has for its object to provide an improved screw compressor arrangement.
  • the screw compressor arrangement should be particularly user-friendly and versatile. It should also be particularly compact and also very low in vibration and noise.
  • the essence of the invention lies in the fact that the output gear is selectively engaged or engageable with the first or second synchronization wheel.
  • the rotors are so independent of a rotational direction of the input shaft by appropriate arrangement of the output gear or corresponding engagement thereof in the conveying direction rotatably driven, so that the air to be compressed is conveyed in the direction of the air outlet.
  • the transmission gear is preferably a spur gear. It is preferably multi-stage, in particular two-stage.
  • the screw compressor arrangement works oil-free. Conveniently, this is air-cooled. It is advantageous if the first rotor and the first rotor shaft are integrally connected to one another. Alternatively, these are carried out separately. Conveniently, the second rotor and the second rotor shaft are integrally formed. Alternatively, these are carried out separately. The rotors preferably work together without contact.
  • axial refers in particular to the respective rotor shaft, and the same applies to the term “radial”.
  • the synchronization wheels arranged on the rotor shafts form a synchronization gear.
  • the synchronization wheels preferably have a different outer diameter. It is advantageous if the first synchronization wheel is smaller than the second synchronization wheel.
  • the size ratio of the synchronization wheels corresponds in particular to the speeds of the rotors.
  • Fig. 1 is a side view of a screw compressor assembly according to the invention; an end view of the screw compressor assembly shown in Figure 1 with the lid removed.
  • Fig. 3 is a section through the screw compressor assembly along the section line
  • a screw compressor arrangement shown in the figures comprises a screw compressor housing 1 and a transmission gear housing 2, which in the assembled state of the screw compressor arrangement is in communication with the screw compressor housing 1.
  • the screw compressor housing 1 is designed in several parts. It has a rotor chamber spatially limiting rotor housing part 3 and a rotor housing part 4 on the rotor housing part 3 frontally angi closed rotor housing part 4 and a removable rotor bearing housing cover 5, which closes the rotor bearing housing part 4 opposite to the rotor housing part 3.
  • the screw compressor housing 1 further has an air inlet 6.
  • the air inlet 6 is formed by an inlet connection 7, which adjoins the rotor housing part 4 opposite to the rotor housing part 3 and opens there into the rotor chamber.
  • the screw compressor arrangement has an air outlet 8, which is in conveying connection with the air inlet 6.
  • the transmission gear housing 2 has a transmission gear housing main part 9 and a removable transmission gear housing cover 10 which closes the gear transmission housing main part 9 frontally.
  • the transmission gear housing main part 9 is preferably formed integrally with the rotor bearing housing part 4, while preferably the transmission gear housing cover 10 is formed integrally with the rotor bearing housing cover 5.
  • a rotor assembly 11 is housed with a first and a male rotor 12 and a second and female rotor 13, respectively.
  • the rotors 12, 13 are arranged in the rotor housing part 3.
  • the first rotor 12 is arranged on a first rotor shaft 14, while the second rotor 13 is arranged on a second rotor shaft 15.
  • the rotor shafts 14, 15 are parallel to each other. They are preferably identically dimensioned or formed.
  • the first rotor 12 has helical profile teeth 16, which engage with corresponding helical profile gaps 17 of the second rotor 13.
  • the first rotor 12 or the first rotor shaft 14 is mounted rotatably or rotatably driven about a first rotor axis 18.
  • a drive-side first bearing assembly 19 and opposite another first bearing assembly 20 are present, so that the first rotor shaft 14 is mounted on both sides or on both sides.
  • the first bearing assembly 19 has a first ball bearing 21 and a first roller bearing 22.
  • the first ball bearing 21 and the first roller bearing 22 are on the first rotor shaft 14 on the drive side arranged. They are also - directly or indirectly - arranged on the rotor bearing housing part 4.
  • the first ball bearing 21 is arranged adjacent to a free first end 23 of the first rotor shaft 14. It rests against an annular shoulder, facing the free first end 23, of the first rotor shaft 14.
  • the first ball bearing 21 is fixed axially there by a first fixing ring 24 which is arranged adjacent to or substantially flush with the free first end 23 on the first rotor shaft 14.
  • the first ball bearing 21 is also arranged on / in a bearing latte 25, which is penetrated by the first rotor shaft 14.
  • the first ball bearing 21 has a first inner ring 26 rotatably mounted on the first rotor shaft 14 and a first outer ring 27 and a plurality of first rolling balls 28 which are held in a first cage 29 of the first ball bearing 21.
  • the first roller bearing 22 is arranged axially spaced from the first rotor 12. It has a rotatably mounted on the first rotor shaft 14 first inner ring 30 and a first outer ring 31 and a plurality of first Wälzrollen 32, which are held in a first cage 33 of the first roller bearing 22.
  • the first rolling rollers 32 extend parallel to the first rotor axis 18.
  • the first outer ring 31 of the first roller bearing 22 is received in the first rotor bearing housing part 4.
  • the rotor bearing housing part 4 has a first annular ridge 34, which runs there radially spaced around the first rotor shaft 14 and protrudes from a supporting wall of the rotor bearing housing part 4 in the direction of the rotor bearing housing cover 5.
  • the support wall extends perpendicular to the first rotor axis 18th
  • first seal assembly 35 Between the first rotor 12 and the first roller bearing 22 sits on the first rotor shaft 14 sealingly a first seal assembly 35.
  • the first seal assembly 35 joins laterally to the first roller bearing 22 at.
  • an externally toothed first synchronization wheel 36 is rotatably mounted on the first rotor shaft 14.
  • the first synchronization wheel 36 of the first rotor 12 and the first rotor shaft 14 is rotatably driven about the first rotor axis 18, which will be discussed in more detail below.
  • the first synchronization wheel 36 abuts the first roller bearing 22 or the first inner ring 30 of the same end face. It is fixed there by a fixing ring which is arranged on the first rotor shaft 14.
  • the first rotor shaft section of the first rotor shaft 14 located on the side of the first synchronization wheel 36 thus forms a first rotor shaft section on the drive side.
  • the first ball bearing 21 has a first shaft diameter WD AI, while the first roller bearing 22 has a first shaft diameter WDR1.
  • the first shaft diameters WDA1 and WDR1 are substantially identical.
  • the first shaft diameter WDR1 is slightly larger than the first shaft diameter WD AI.
  • the first ball bearing 21 has a first nominal width BAI, while the first roller bearing 22 has a first nominal width BR1.
  • the first nominal widths BAI and BR1 of the first bearings 21, 22 are essentially the same size.
  • first distance AI Between the free first end 23 of the first rotor shaft 14 and the first ball bearing 21 is an axial first distance AI, which is smaller than the first nominal width BAI or BR1 of the first bearing 21, 22.
  • first distance AA1 Between the first ball bearing 21 and the first roller bearing 22 there is an axial first distance AA1, which is substantially larger than the first nominal width BAI or BR1 of the first bearings 21, 22.
  • the first distance AA1 is approximately three times as large as the nominal width BAI or BR1 of the first bearing 21, 22.
  • the first rotor shaft 14 has a further first rotor shaft section, which is mounted in the further first bearing arrangement 20.
  • the further first bearing arrangement 20 is in the rotor Housing part 3, in particular in the end wall opposite the rotor bearing housing part 4, received and sitting on the other first rotor shaft piece.
  • the further first bearing arrangement 20 has a further first ball bearing 37 and a further first roller bearing 38, which is arranged directly adjacent to the further first ball bearing 37.
  • first clamping plate 39 laterally, which is fixed by means of a first clamping screw 40 frontally on the first rotor shaft 14 at the other first rotor shaft piece.
  • the first clamping screw 40 is there screwed axially into the first rotor shaft 14.
  • the further first ball bearing 37 has a first inner ring 41, arranged rotatably on the first rotor shaft 14, and a first outer ring 42 and a multiplicity of first rolling balls 43, which are held in a first cage 44 of the further first ball bearing 37.
  • the further first roller bearing 38 is arranged between the further first ball bearing 37 and the first rotor 12. It rests against an annular shoulder of the first rotor shaft 14 facing the further first ball bearing 37. It has a first inner ring 45 rotatably mounted on the first rotor shaft 14 and a first outer ring 46 and a multiplicity of first rolling rollers 47, which are held in a first cage 48 of the further first roller bearing 38.
  • the first rolling rollers 47 extend parallel to the first rotor axis 18.
  • a spacer ring 120 is disposed on the first rotor shaft 14.
  • a spring assembly 121 preferably comprising Wellfederin arranged.
  • the further first roller bearing 38 bears laterally against a first sealing ring 49, which bears against the rotor housing part 3 and ends adjacent to the first rotor shaft 14. Furthermore, a first air seal 50 is present, which bears sealingly against the rotor housing part 3, the first rotor shaft 14 and the first sealing ring 49.
  • the further first ball bearing 37 and the further first roller bearing 38 have an identical shaft diameter WDWl. Furthermore, they essentially have an identical axial nominal width BW1.
  • At least two adjustment members 126 are inserted between the outer ring 27 of the first ball bearing 21 and the bearing latte 25 to adjust an axial gap of the first rotor 12 (Fig. 7, 12).
  • Each adjustment member 126 is conveniently designed sickle-like.
  • Two adjusting elements 126 favorably form a dial, allowing adjustment of the axial gap with the ball bearing 21 mounted.
  • the number of shims is selected, which are then arranged in series.
  • the second rotor 13 or the second rotor shaft 15 is mounted rotatably or rotatably driven about a second rotor axis 51.
  • a drive-side second bearing arrangement 52 and opposite another second bearing arrangement 53 are present, which are essentially identical to the first bearing arrangement 19 or the further first bearing arrangement 20.
  • the second rotor shaft 14 is thus likewise mounted on both sides or on both sides.
  • the second bearing assembly 52 has a second ball bearing 54 and a second roller bearing 55.
  • the second ball bearing 54 and the second roller bearing 55 are arranged on the drive side on the second rotor shaft 15. They are also - directly or indirectly - arranged on the rotor bearing housing part 4.
  • the second ball bearing 54 is arranged adjacent to a free second end 57 of the second rotor shaft 15. It rests against an annular shoulder, facing the free second end 57, of the second rotor shaft 15.
  • the second ball bearing 54 is fixed axially there by a second fixing ring 56 which is adjacent or arranged substantially flush with the free second end 57 on the second rotor shaft 15.
  • the second ball bearing 54 is also arranged on / in the bearing plate 25, which is penetrated by the second rotor shaft 15.
  • the second ball bearing 54 has a second inner ring 58 rotatably mounted on the second rotor shaft 15 and a second outer ring 59 and a plurality of second rolling balls 60, which are held in a second cage 61 of the second ball bearing 54.
  • the second roller bearing 55 is arranged axially spaced from the second rotor 13. It has a second inner ring 62 arranged in a rotationally fixed manner on the second rotor shaft 15 and a second outer ring 63 and a multiplicity of second rolling rollers 64 which are held in a second cage 65 of the second roller bearing 55.
  • the second rolling rollers 64 extend parallel to the second rotor axis 15.
  • the second outer ring 63 of the second roller bearing 55 is received in the rotor bearing housing part 4.
  • the rotor bearing housing part 4 has a second annular web 66, which runs there radially spaced around the second rotor shaft 15 and protrudes from the supporting wall of the rotor bearing housing part 4 in the direction of the rotor bearing housing cover 5.
  • the support wall extends perpendicular to the second rotor axis 51 to form an axial gap adjacent to the second rotor 13.
  • the second seal assembly 67 closes laterally to the second roller bearing 55 at.
  • an externally toothed second synchronization wheel 68 is rotatably mounted on the second rotor shaft 15.
  • the second synchronization wheel 68 of the second rotor 13 and the second rotor shaft 15 is rotatably driven about the second rotor axis 51, which will be discussed in more detail below.
  • the second synchronization wheel 68 abuts the second roller bearing 55 or the second inner ring 62 of the same frontally. It is fixed there by a fixing ring, which is arranged on the second rotor shaft 15.
  • the first rotor shaft section of the second rotor shaft 15 located on the side of the second synchronization wheel 68 thus forms a second rotor shaft section on the drive side.
  • the second ball bearing 54 has a second shaft diameter WDA2, while the second roller bearing 55 has a second shaft diameter WDR2.
  • the second shaft diameters WDA2 and WDR2 are substantially identical. They correspond to the first shaft diameters WDA1 or WDR1.
  • the second shaft diameter WDR2 is slightly larger than the second shaft diameter WDA2.
  • the second ball bearing 54 has a second nominal width BA2, while the second roller bearing 55 has a second nominal width BR2.
  • the second nominal widths BA2 and BR2 of the second bearings 54, 55 are substantially the same size. They correspond to the first nominal widths BAI or BR1.
  • the second distance A2 corresponds to the first distance AI.
  • the second distance AA2 is greater than the second nominal width BA2 or BR2 of the second bearing 54, 55.
  • the second distance AA2 is about three times as large as the nominal width BA2 or BR2 of the second bearing 54, 55.
  • the axial second distance AA2 corresponds to the first distance AA1.
  • the second rotor shaft 15 has a further second rotor shaft section, which is mounted in the further second bearing arrangement 53.
  • the further second bearing arrangement 53 is essentially identical to the further first bearing arrangement 20.
  • the further second bearing arrangement 53 has a further second ball bearing 69 and a further second roller bearing 70, which is arranged directly adjacent to the further second ball bearing 69.
  • a second clamping plate 71 laterally, which is fixed by means of a second clamping screw 72 frontally on the second rotor shaft 15 at the other second rotor shaft piece.
  • the second clamping screw 72 is there screwed axially into the second rotor shaft 15.
  • the further second ball bearing 69 has a second inner ring 73 arranged in a rotationally fixed manner on the second rotor shaft 15 and a second outer ring 74 and a multiplicity of second rolling balls 75 which are held in a second cage 76 of the further second ball bearing 69.
  • the further second roller bearing 70 is arranged between the further second ball bearing 69 and the second rotor 13. It bears against an annular shoulder of the second rotor shaft 15 facing the further second ball bearing 69. It has a second inner ring 77, arranged rotatably on the second rotor shaft 15, and a second outer ring 78 and a multiplicity of second rolling rollers 79, which are held in a second cage 80 of the further second roller bearing 70.
  • the second rolling rollers 79 extend parallel to the second rotor axis 51.
  • a spacer ring 122 is disposed on the second rotor shaft 14.
  • a spring assembly 123 typically comprising corrugated spring washers arranged.
  • the further second roller bearing 70 bears laterally against a second sealing ring 81, which bears against the rotor housing part 3 and ends adjacent to the second rotor shaft 15.
  • a second air seal 82 is present, which bears sealingly against the rotor housing part 3, the second rotor shaft 15 and the second sealing ring 81.
  • the further second ball bearing 37 and the further first roller bearing 38 have an identical shaft diameter WDW2, which corresponds to the shaft diameter WDW1 of the other first bearings 37, 38. Furthermore, they essentially have an identical axial nominal width BW2.
  • the first rotor shaft 14 has a first hydraulic pressure port 118.
  • the second rotor shaft 15 has a second hydraulic pressure port 119.
  • At least two adjusting members 127 are interposed between the outer ring 59 of the second ball bearing 54 and the bearing plate 25 to adjust an axial gap of the second rotor 13.
  • Each adjustment member 127 is conveniently sickle-like and designed according to the adjustment member 126.
  • Two adjusting elements 127 favorably form a dial, which allows adjustment of the axial gap with the ball bearing 54 mounted. Depending on the required axial gap, the number of shims is selected, which are then arranged in series.
  • the rotor assembly 11 is a transmission gear 83 upstream.
  • the transmission gear 83 is housed in the transmission gear housing 2.
  • the transmission gear 83 includes an externally toothed output gear 84 which meshes with and is substantially larger than the first timing gear 36 in a first arrangement.
  • the output gear 84 is slightly smaller than the second synchronization 68.
  • the driven gear 84 is rotatably mounted on an intermediate shaft 85, which is rotatably mounted or rotatably drivable in the transmission case 2.
  • a first tapered roller bearing 86 and a second tapered roller bearing 87 are provided, which are identical.
  • the first tapered roller bearing 86 has a first tapered roller bearing inner ring 88 and a first tapered roller bearing outer ring 89 and a plurality of first tapered rollers 90.
  • the second tapered roller bearing 87 has a second tapered roller bearing inner ring 91 and a second tapered roller bearing outer ring 92 and a plurality of second tapered rollers 93.
  • the tapered roller bearing inner rings 88, 91 are rotatably mounted on the intermediate shaft 85, while the tapered roller bearing outer rings 89, 92 are arranged on the transmission gear housing 2.
  • the tapered rollers 90, 93 of the tapered roller bearings 86, 87 run at an angle to each other. They are arranged according to an X arrangement.
  • the tapered roller bearings 86, 87 are each end-side arranged on the intermediate shaft 85.
  • the nominal widths of the tapered roller bearings 86, 87 are conveniently identical. Their bore diameter is preferably identical.
  • the second tapered roller bearing 87 four spring rings 98 are assigned, which are arranged there end to the intermediate shaft 85.
  • an external gear intermediate gear 94 adjacent to the output gear 84 is rotatably mounted on the intermediate shaft 85.
  • the intermediate gear 94 is substantially smaller than the output gear 84. It is slightly smaller than the first sync wheel 36 and substantially smaller than the second sync wheel 68.
  • the intermediate shaft 85 is in the transmission gearbox housing cover 10 associated with a mounting opening 95, which is closed, for example, by a removable intermediate shaft mounting cover 96 as shown in FIG.
  • the intermediate gear 94 is engaged with an externally toothed input gear 99, which is the largest gear of the transmission gear 83 and is substantially larger than the intermediate gear 94.
  • the input gear 99 is rotatably mounted on a rotatably driven or rotatable input shaft 100.
  • the input shaft 100 is rotationally driven by means of two tapered roller bearings 101, 102 rotatably mounted in the transmission gear housing 2.
  • the first tapered roller bearing 101 has a first tapered roller bearing inner race 103 rotatably mounted on the input shaft 100 and a first tapered roller bearing outer race 104 and a plurality of first tapered rollers 105 interposed therebetween.
  • the second tapered roller bearing 102 has a second tapered roller bearing inner ring 106 rotatably mounted on the input shaft 100 and a second tapered roller bearing outer race 107 and a plurality of second tapered rollers 108 interposed therebetween.
  • the first tapered roller bearing outer race 104 is disposed in the transmission gear housing cover 10.
  • the second tapered roller bearing outer ring 107 is disposed in the transmission gear case main body 9.
  • the tapered rollers 105, 108 run obliquely to each other.
  • the tapered roller bearings 101, 102 are arranged according to an X arrangement.
  • the nominal widths of the tapered roller bearings 101, 102 are favorably identical. It is advantageous if the first tapered roller bearing 101 has a smaller bore diameter than the second tapered roller bearing 102.
  • the first tapered roller bearing 101 four spring rings 124 are assigned, which are arranged there end to the input shaft 100. Adjacent to the second tapered roller bearing 102, two shims or spacers 125 are disposed on the input shaft 100.
  • an input shaft mounting opening 109 is formed adjacent to the input shaft 100, which is closed according to Figure 3, for example by an input shaft mounting cover 110.
  • the input shaft 100 carries an oil pump unit 117.
  • the input shaft 100 protrudes opposite to the transmission gear housing cover 10 from the transmission gear housing main part 9. There is to the input shaft 100th an outer drive shaft (not shown) coupled.
  • the coupling can be done directly or indirectly, for example via a belt.
  • the drive shaft is for example a motor shaft or propeller shaft of a silo vehicle. It is for example part of a hydraulic unit on a silo vehicle.
  • At the projecting end of the input shaft 100 may also be arranged a cooling fan.
  • the rotor shafts 14, 15, the intermediate shaft 85 and the input shaft 100 are parallel to each other.
  • the rotor shafts 14, 15 run in a plane.
  • the intermediate shaft 85 is disposed between the input shaft 100 and the rotor shafts 14, 15.
  • the input shaft 100 may protrude on both sides on the housing 2. Thereby, it is possible to drive the input shaft 100 from both sides.
  • the first tapered-roller bearing 101 and the second tapered-roller bearing 102 are designed identically, ie in particular have identical bore diameters.
  • the screw compressor assembly comprises a total of exactly five gears, namely the two synchronization wheels 36, 68, the output gear 84, the intermediate gear 94 and the input gear 99.
  • the transmission 83 includes the output gear 84, the Intermediate gear 94 and the input gear 99.
  • the operation of the screw compressor assembly will be described below.
  • the input shaft 100 is rotated by the rotating connected drive shaft in a first input shaft rotation direction 111.
  • the rotationally fixed on the input shaft 100 input gear 99 is set in corresponding rotation.
  • the intermediate gear 94 and the intermediate shaft 85 supporting it are rotated with the rotationally fixed output gear 84 in a first intermediate shaft rotation direction 112 that is opposite to the first Input shaft rotation direction 111 is.
  • the output gear 84 meshing therewith meshes with the first synchronization wheel 36 and thus displaces the first synchronization wheel 36 and the first rotor shaft 14 or the first rotor 12 supporting it in a first synchronization gear Rotor shaft rotation direction 113 in rotation.
  • the first rotor shaft rotation direction 113 of the rotor 13 is opposite to the first intermediate shaft rotation direction 112.
  • the second synchronization wheel 68 and the second rotor shaft 15 or the second rotor 13 carrying it are set in rotation in a second rotor shaft rotation direction 114. There is a translation into slow.
  • the rotor shafts 14, 15 rotate in opposite directions.
  • the input shaft 100 and the first rotor shaft 14 rotate in the same direction.
  • the intermediate shaft 85 and the second rotor shaft 15 also rotate in the same direction.
  • the intermediate shaft 85 is now due to its coupling with the input shaft 100 in rotation in an opposite second intermediate shaft rotation direction 116 in rotation, which is opposite to the first intermediate shaft rotation direction 112.
  • the input shaft 100 including input gear 99 is offset, in particular along a height direction, in particular vertical direction, according to FIG. 5.
  • lateral displacement of the input shaft 100 is also conceivable. that is, along a horizontal direction or diagonal direction, when the distance of the input shaft 100 to the rotor shafts 14, 15 is thereby increased.
  • the input shaft 100 together with the input gear 99 has a greater distance from the rotor shafts 14, 15.
  • the staggered arrangement of the input shaft 100 with the input gear 99 is achieved in particular by correspondingly offset a receiving bore in the transmission gear housing main part 9 for the second tapered roller bearing outer ring 107 and in the transmission gear housing cover 10 for the first tapered roller bearing outer ring 104 are arranged.
  • the transmission gear housing cover 10 and the transmission gear housing main part 9 are used with corresponding receiving bores.
  • an offset arrangement of the intermediate shaft 85 is made possible by the fact that bearing bores in the transmission gearbox housing cover 10 and the transmission gearbox housing main part 9 for the tapered roller bearing outer rings 89, 92 are correspondingly positioned differently.
  • the intermediate shaft 85 together with the output gear 84 and the intermediate gear 99 are offset laterally.
  • the intermediate shaft 85 together with output gear 84 and intermediate gear 99 is offset in the direction of the second rotor shaft 15.
  • the intermediate shaft 85 together with the output gear 84 and intermediate gear 99 is displaced away from the first rotor shaft 14.
  • the second tapered roller bearing 87 is assigned two shims 97, which are arranged there on the intermediate shaft 85 at the end.
  • the first tapered roller bearing 101 are now associated with two shims 125, which are arranged there on the end side of the input shaft 100. Adjacent to the second tapered roller bearing 102, four spring rings 124 are disposed on the input shaft 100.
  • the rotor shafts 14, 15 remained unchanged in orientation with respect to their position.
  • the transmission gear housing 2 is processed accordingly different.

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

Abstract

L'invention concerne un système de compresseur à vis qui comporte un compresseur à vis doté d'un ensemble rotor (11) pour comprimer de l'air. L'ensemble rotor (11) comprend un premier rotor (12) qui est monté sur un premier arbre de rotor (14) ainsi qu'un second rotor (13) qui est monté sur un second arbre de rotor (15). Ledit compresseur à vis présente également un mécanisme de synchronisation (36, 68) pour assurer l'entraînement synchronisé des rotors (12, 13). Ledit mécanisme de synchronisation (36, 68) comprend une première roue de synchronisation (36) montée sur le premier arbre de rotor (14) et une seconde roue de synchronisation (68) qui est montée sur le second arbre de rotor (15). Le système de compresseur à vis comprend en outre un mécanisme multiplicateur (83) qui présente un arbre d'entrée (100) sur lequel est monté une roue d'engrenage d'entrée (99). Le mécanisme multiplicateur (83) présente également un arbre intermédiaire (85) sur lequel est montée une roue d'engrenage intermédiaire (94) qui s'engrène avec la roue d'engrenage d'entrée (99), ainsi qu'une roue d'engrenage de sortie (84) pouvant être montée de sorte à s'engrener sélectivement avec la première ou la seconde roue de synchronisation (36, 38).
PCT/EP2018/058813 2017-04-11 2018-04-06 Système de compresseur à vis, à engrenage de synchronisation et à engrenage de transmission WO2018189041A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017206240.1 2017-04-11
DE102017206240.1A DE102017206240B3 (de) 2017-04-11 2017-04-11 Schraubenverdichteranordnung

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WO2018189041A1 true WO2018189041A1 (fr) 2018-10-18

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PCT/EP2018/058813 WO2018189041A1 (fr) 2017-04-11 2018-04-06 Système de compresseur à vis, à engrenage de synchronisation et à engrenage de transmission

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WO (1) WO2018189041A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018113043A1 (de) * 2018-05-31 2019-12-05 FRISTAM Pumpen Schaumburg GmbH Rotierende Verdrängerpumpe

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3256745A (en) * 1963-08-16 1966-06-21 Gulf Kramer Corp Reversing power transmission
US20110293444A1 (en) * 2008-12-19 2011-12-01 Mouvex Device for pressurizing a fluid, to be directly mounted on a power take-off

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29904411U1 (de) 1999-03-10 2000-07-20 GHH-RAND Schraubenkompressoren GmbH & Co. KG, 46145 Oberhausen Schraubenkompressor
US8342829B2 (en) 2005-12-08 2013-01-01 Ghh Rand Schraubenkompressoren Gmbh Three-stage screw compressor

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3256745A (en) * 1963-08-16 1966-06-21 Gulf Kramer Corp Reversing power transmission
US20110293444A1 (en) * 2008-12-19 2011-12-01 Mouvex Device for pressurizing a fluid, to be directly mounted on a power take-off

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