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
  • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
  • F01C21/02—Arrangements of bearings
• • 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
  • F04C29/04—Heating; Cooling; Heat insulation
• • 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
  • F04C2240/40—Electric motor
  • F04C2240/402—Plurality of electronically synchronised motors
• • 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
  • F04C2240/50—Bearings
  • F04C2240/51—Bearings for cantilever assemblies

Definitions

• the invention is therefore based on the object, a screw compressor in To provide the preamble of claim 1 type, in which the rotors are cooled independently of the conveyed medium in such a way that good conditions are created for a small game between the rotors among themselves and between the rotors and the pump chamber housing, without it from susceptible to failure ⁇ seals required.
• the solution according to claim 1 is composed of two components, namely firstly the feature that the displacement rotors are cooled more on the pressure side than on the suction side, and secondly a cooling technology using the special design of the rotor bearing.
• Multi-stage rotors are to be understood as those whose screw threads forming the compression chambers revolve the rotor several times, so that a plurality of compression chambers are formed over the rotor length, in each case on the suction and pressure sides.
• the screw turns revolve three times around the associated rotor.
• the number of stages can be determined in accordance with the respective printing area. At least five stages are preferably used.
• the invention uses a special technology adapted to the type.
• This type of construction presupposes that each displacement rotor is mounted in a floating manner on a stationary bearing tube which surrounds the rotor shaft and at least one rotor-side bearing and projects into the rotor. Only this is cooled directly, while the cooling of the rotor takes place indirectly by the mutually opposing peripheral surfaces of the rotor and the bearing body being heat exchangeable to one another. are ordered.
• the bearings and the rotor shaft are particularly well cooled because they are located within the bearing tube.
• the intermediate space should not be connected to the suction side but to the pressure side.
• the surfaces can also be provided with elevations and depressions which improve the heat transfer coefficient to the medium located therebetween.
• the mutual distance between the two surfaces should be as small as possible.
• such a treatment of the surfaces can be provided that they have a high absorption number in the area of thermal radiation.
• the heat transfer to the opposing surfaces of the rotor and the bearing body can also be improved in that the gas located between them is caused to flow.
• the intermediate space can be connected to a gas source.
• the gas flow can also be used for heat dissipation if the gas temperature is selected accordingly (cooling if necessary).
• he can, if necessary, exercise a blocking function to protect the bearing and drive area from the access of the conveying medium or of substances contained in the conveying medium.
• the gas used is expediently fed to the pressure side of the machine.
• the interacting surfaces of the rotor and bearing body can be equipped with conveying elements to convey the gas. This can make it unnecessary to provide an external source of pressurized gas. This also applies if the gas supplied is primarily intended to serve as a blocking and not for cooling purposes.
• the conveying effect of the surfaces can be brought about in particular by equipping them with a conveying thread on one or both sides. Instead of or in addition, they can also be conical, so that the centrifugal force is used for the promotion. Such means promoting the movement of the gas in the intermediate space are also useful for improving the heat transfer when no additional gas supply is provided.
• the part of the bearing body protruding into the rotor cavity is expediently equipped with channels through which cooling liquid flows, which are preferably arranged close to the circumferential surface of the bearing body opposite the rotor.
• the housing may be intensively cooled or at least kept at a predetermined temperature without the risk of the rotor starting up on the housing due to thermal play.
• the efficiency of the pump can be increased by the cooling effect exerted on the pumped medium in this way.
• pre-admission It is known in particular in the case of vacuum pumps to allow gas under higher pressure to flow into the compression cells of the machine in order to cool the conveying medium and / or to reduce noise.
• This technique referred to as pre-admission, is also advantageously used in connection with the invention.
• chilled gas from a suitable source can be used.
• An external heat exchanger can be avoided by leading the pre-inlet gas through a heat exchanger located in the cooling chamber on the housing side.
• liquid can also be added in the scooping chamber, which evaporates there and thereby extracts heat from the medium being conveyed.
• the cooling of the bearing body at least in the area in which it is located in the heat influence of the rotor, has the great advantage that rolling bearings can be used which are permanently lubricated with grease and are therefore particularly low-maintenance and do not pose a risk of contamination for the delivery space .
• the above-mentioned possibility of equipping the interacting surfaces of the rotor and bearing body with conveying elements can be used to protect the bearing area from foreign substances that could come from the scooping area.
• the cooperating conveying members are designed with the conveying direction leading out of the rotor cavity.
• This effect is increased by connecting the rotor cavity to a flushing or sealing gas source. Thanks to the promotional effect, this source need not be under pressure; however, this is not out of the question.
• the gas can also serve cooling purposes.
• the cleaning liquid should, as far as it can get into the suction chamber, have a vapor pressure below the suction pressure. If the pump is multi-stage and the contamination (for example, depending on the pressure) is mainly reflected in the second and / or subsequent stages, there is the possibility of limiting the injection of the cleaning liquid to the second or subsequent stage and thereby to separate the suction side.
• the flange plates 50 which in the example shown consist of one piece with the bearing bodies 7, are placed on the top of the base plate 3 with their outer edges 51, which essentially follow the circumference of the suction chamber housing 4, and their abutting inner edges 52.
• the flange plates 50 are sealed with respect to the base plate 3.
• the flange plates 50 Underneath the flange plates 50, between the edges 51, 52, there is a recess which, with the top of the base plate 3, encloses a space 39 which serves to accommodate synchronization gearwheels 40 which are rotatably fixed on the shafts by known means 20 are arranged between the bearings 21 and the motor rotors. So that they can mesh with each other in the area of the inner edges 52 of the flange plates 50, the inner edges have a cutout at a corresponding point through which the gearwheels pass.
• a web remains on each side, to which the reference line in FIG. 1 refers to the reference number 52 which generally designates the inner edge. This web is advantageous not only for reasons of stability, but also because it enables a circumferential seal on the one hand with respect to the base plate 3 and on the other hand between the flattened secant surfaces of the flange plates 50.
• the recesses 39 in the flange plates 50 have a diameter that is larger than the diameter of the synchronization gears 40. They are arranged a little eccentrically in relation to the inner edges 52, so that the synchronization gears 40 despite the assembly of the rotor units the presence of the sealing web at 52 can be used.
• the synchronization gearwheels 40 can also serve as pulse encoder disks or can be supplemented by additional pulse encoder disks which are sensed by sensors 42, one of which is shown in FIG.
• These sensors 42 are connected to a control device which monitors the respective rotational position of the rotors with respect to a target value and corrects them via the drive. It is a matter of electronic synchronization of the rotors, which is known as such and therefore does not require any further explanation here.
• the play between the teeth of the synchronization gears 40 is slightly less than the backlash between the displacement projections 9 of the rotors 8. However, it is greater than the synchronization tolerance of the electronic synchronization device. If the latter function properly, neither the flanks of the displacement projections 9 nor the teeth of the synchronization gears 40 come into contact with one another. In the event that the latter should come into contact with one another, they are provided with a wear-resistant and possibly low-friction coating.
• the performance data of the pump are determined by the displacement or delivery volume formed on the rotors and thus by the length of the rotors.
• the delivery data can therefore be changed by changing the length of the pump part containing the rotors.
• a series of pumps with different performance data is therefore preferably characterized in that the individual pumps of this series differ in the gradation of the length of these parts, to which the pump chamber housing, the rotors and, if applicable, the tubular parts of the projecting into the rotors Bearing body belong.
• each rotor with the associated bearing and drive devices forms an independently mountable structural unit which, in addition to the rotor, comprises the bearings 21, 22, the bearing body 7, the cooling devices provided therein, the shaft 20, the synchronization gear 40, the associated sensor 42 and the motor rotor 35.
• These units are completely pre-assembled in the pump. They can be easily removed or inserted from the base plate 3 after the removal of the pumping chamber housing. Their replacement can therefore be left to the user, while the manufacturer takes care of the maintenance of the sensitive units as such.
• the pump is preferably of an isochoric design in order to be able to convey larger quantities of liquid without damage.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Applications Or Details Of Rotary Compressors (AREA)
• Structures Of Non-Positive Displacement Pumps (AREA)
• Rotary Pumps (AREA)

Applications Claiming Priority (5)

Publications (3)

Family

ID=26016151

Family Applications (1)

Country Status (12)

Cited By (1)

Families Citing this family (26)

Family Cites Families (10)

• 1996
  • 1996-06-18 DK DK96922831T patent/DK0834018T4/da active
  • 1996-06-18 ES ES96922831T patent/ES2141515T5/es not_active Expired - Lifetime
  • 1996-06-18 US US08/981,322 patent/US5924855A/en not_active Expired - Fee Related
  • 1996-06-18 PT PT96922831T patent/PT834018E/pt unknown
  • 1996-06-18 JP JP50357097A patent/JP3965507B2/ja not_active Expired - Fee Related
  • 1996-06-18 DE DE59603870T patent/DE59603870D1/de not_active Expired - Lifetime
  • 1996-06-18 WO PCT/EP1996/002631 patent/WO1997001038A1/fr not_active Ceased
  • 1996-06-18 AT AT96922831T patent/ATE187528T1/de not_active IP Right Cessation
  • 1996-06-18 EP EP96922831A patent/EP0834018B2/fr not_active Expired - Lifetime
  • 1996-06-18 KR KR1019970709576A patent/KR100424386B1/ko not_active Expired - Fee Related
  • 1996-06-19 TW TW085107398A patent/TW377384B/zh not_active IP Right Cessation
• 2000
  • 2000-02-16 GR GR20000400381T patent/GR3032683T3/el unknown

Non-Patent Citations (1)

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