WO2008062023A1 - Machine volumétrique rotative - Google Patents

Machine volumétrique rotative Download PDF

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Publication number
WO2008062023A1
WO2008062023A1 PCT/EP2007/062657 EP2007062657W WO2008062023A1 WO 2008062023 A1 WO2008062023 A1 WO 2008062023A1 EP 2007062657 W EP2007062657 W EP 2007062657W WO 2008062023 A1 WO2008062023 A1 WO 2008062023A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
working
displacement machine
conveyor
chamber
Prior art date
Application number
PCT/EP2007/062657
Other languages
German (de)
English (en)
Inventor
Johann Sagawe
Gottfried Sagawe
Original Assignee
Johann Sagawe
Gottfried Sagawe
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 Johann Sagawe, Gottfried Sagawe filed Critical Johann Sagawe
Publication of WO2008062023A1 publication Critical patent/WO2008062023A1/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
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/088—Elements in the toothed wheels or the carter for relieving the pressure of fluid imprisoned in the zones of engagement
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • 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
    • 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
    • F04C2/18—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 similar tooth forms
    • 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
    • F04C2240/70—Use of multiplicity of similar components; Modular construction

Definitions

  • the invention relates to a Umlaufverdrängermaschine, in particular a hydraulic thoroughlyenzahnradmotor and a hydraulic external gear pump, wherein a central AbInstitutsc. Drive gear is provided along the circumference of a plurality of conveyor gears are arranged.
  • the circulation displacement machine preferably has a modular construction, wherein the individual modules can be switched on as needed.
  • Displacement machines are hydraulic machines (pumps, motors) in which a hydrostatic power conversion takes place according to the displacement principle.
  • the rotary displacement machines the conveying process takes place in the circumferential direction.
  • at least two intermeshing toothed wheels are typically driven by a pressurized pressure medium (usually a fluid or working fluid) (hydraulic gear motor) or driven by an external drive (hydraulic toothed wheel pump) for delivery of the fluid.
  • the performance of a recirculating displacement machine in addition to its design-related operation, in particular also determined by the pressure difference between the high-pressure and the low-pressure zone of the machine.
  • the performance of the respective application can be adjusted.
  • the maximum power of a gear machine is limited primarily by the load capacity of the machine parts involved. Excessive load on these parts can destroy the machine. Since it is not possible in the example operated as a gear motor conventional Umlaufverdrängermaschine, the performance through Increasing the fluid pressure to increase arbitrarily, the machine must be sized accordingly large to achieve a higher performance.
  • the object of the invention is to provide a circulation displacement machine with a high performance. It is another object of the invention to provide a Umlaufverdrängermaschine that allows flexible use. This object is achieved by a circulation displacement machine according to claim 1. Furthermore, the invention is achieved by a housing according to claim 19 and an external gear according to claim 21. Further advantageous embodiments of the invention are specified in the dependent claims.
  • a recirculating displacement machine having a housing and a first external gear pair disposed in a working chamber of the housing, the gear pair being formed of a work gear and a first feed gear.
  • the first conveying gear has a first combing area together with the working gear.
  • a first supply channel for a working fluid is provided, which opens into the working chamber in a region near the first combing region.
  • a first outlet channel for the working fluid also opens into the working chamber in a region near the first combing area.
  • a second externally toothed conveying gear wheel is arranged in the working chamber, which with the work gear forms a second externally toothed gear pair with a common second combing area.
  • a second inlet channel for the working fluid opens into the working chamber in a region near the second combing region
  • a second outlet channel for the working fluid opens into the working chamber in a region near the second combing region on the side of the second combing region opposite the second inlet channel.
  • the first inflow channel and the second inflow channel are fluidly connected in this way.
  • the two pairs of gears each formed from a conveyor gear and the working gear form two hydraulic machines interacting with each other.
  • the use of a common drive gear allows the hydraulic machines to be coupled, thereby increasing the performance of the entire recirculating displacement machine.
  • the use of a common drive gear also leads to material savings and weight reduction, since only a single work gear and a single housing is necessary. Since only one drive or output shaft also has to be led out of the housing, this arrangement also requires only an elaborate seal for the corresponding shaft.
  • a third externally toothed conveyor gear is arranged in the working chamber, which forms with the work gear a third gear pair with a common third combing area.
  • a third inlet channel for the working fluid in the combing area opens into the working chamber, while a third outlet channel for the working fluid opens into the working chamber on the side of the third combing area opposite the third inlet channel.
  • the second inlet channel and the third outlet channel communicate fluidically with one another in such a way that a portion of the working fluid flowing into the working chamber through the second inlet channel is transported from the working gear to the third outlet channel.
  • the work gear is formed as a central gear, along the circumference at least three conveyor gears ange- which mesh with the working gear.
  • uniform distribution of the conveyor gears along the circumference of the drive gear uniform loading of the drive gear and the drive shaft can be achieved. This has a positive effect on the service life of the machine.
  • the working gear has a same or a smaller diameter than the conveyor gears.
  • the speed of these gears can be reduced. This results in a quieter run.
  • the larger conveyor gears can also produce greater torque.
  • a further advantageous embodiment of the invention provides that the working gear has a substantially larger diameter than the conveyor gears.
  • this allows a plurality of conveyor gears along the circumference of the drive gear can be arranged, whereby a relatively high performance can be achieved.
  • this allows a better sealing of the drive shaft, since this shaft is located farther away from the high-pressure regions formed in the mouth regions of the inlet channels of the individual toothed wheel pairs due to the relatively large diameter of the working toothed wheel.
  • the feed channel assigned to a gear pair opens onto the combing area of the respective gear pair and opens into the working chamber.
  • a favorable supply of the working fluid is achieved in the working chamber.
  • the mouth opening of the feed pair associated with a gear pair is arranged in the bottom surface of the working chamber. Due to the different arrangement of the inlet and the drain channels, the Conveyor gears are placed close to each other without their inlet and outlet channels interfere with each other. The arrangement of the flow channel in the bottom surface of the working chamber immediately at the edge of the combing area proves to be favorable for the flow of the working fluid.
  • a particularly advantageous embodiment of the invention provides that a screen element is arranged on the side of a combing region facing the inlet channel.
  • This shielding element makes it possible to shield the combing area from the working fluid flowing into the working chamber. As a result, disturbing turbulence can be avoided, which typically arise due to the rotation of the gears in the flowing fluid.
  • the shielding element has a vertical impact surface for the working fluid.
  • a baffle surface allows advantageous guidance of the flowing working fluid.
  • a particularly advantageous embodiment of the invention provides that the shield element has a wedge-shaped region which engages between the feed gear and the working gear wheel.
  • the associated combing area can be shielded particularly effectively from the incoming working fluid.
  • the working fluid only reaches the interdental spaces of the rotating toothed wheels in the regions not covered by the shielding element. This avoids turbulence and favors the flow of the working fluid. In particular, by reducing turbulence, the efficiency of the machine can be improved.
  • the teeth of the conveyor gears have a reduced compared to the teeth of the working gear in the operation of the machine as a motor height, which by the ge Genendes engagement of the teeth of the feed gear and the work gear in the interdental spaces of the work gear residual volume formed is increased.
  • the increased residual volume makes it possible to return part of the working fluid from the discharge channel via the combing area to the inlet channel.
  • the fluid consumption of the gear motor can be reduced.
  • the speed of the engine can be increased in this way.
  • the housing is modular, wherein a module comprises a conveyor gear, which forms a pair of gears with a common Kämm Scheme together with the working gear.
  • a module comprises a conveyor gear, which forms a pair of gears with a common Kämm Scheme together with the working gear.
  • a further advantageous embodiment of the invention provides that a module of the rotary displacement machine can be switched on and off separately in order to set a desired power. As a result, the performance of the machine can be adapted without modification of the respective application.
  • Figure 1 shows a Umlaufverdrängermaschine invention with a central working gear and three arranged along the circumference of the work gear conveyor gears.
  • FIG. 2 shows a housing of the rotary displacement machine according to the invention with an inner working chamber
  • FIGS. 4A and 4B show two variants of a further embodiment of the rotary displacement machine according to the invention with four symmetrically arranged around a central drive gear conveyor gears and a modular housing.
  • Fig. 5 shows a further embodiment of the rotary displacement machine according to the invention with three symmetrically arranged around a small drive gear conveyor gears;
  • FIG. 6 is a perspective view of a conveyor gear according to the invention for a rotary displacement machine.
  • FIG. 1 shows by way of example the structure of a rotary displacement machine according to the invention.
  • a rotary displacement machine such as a hydraulic gear motor or a hydraulic gear pump, has a housing 1. Inside the housing 1, a working chamber 2 for receiving a plurality of external gears is formed.
  • the working chamber 2 forms a closed fluid space which is decoupled from the environment by the housing wall. It is formed by cylindrical recesses in the housing 1, which serve as sub-chambers for receiving a respective gear.
  • In the present embodiment of the invention are in the working chamber 2 four intermeshing external gears 3,4,5,6 arranged. These are preferably by means of appropriate bearings, such as sliding or rolling bearings, rotatably mounted in the housing 1 of the machine.
  • a first external gear 3 forms a central working gear, which is connected to a shaft 31.
  • the preferably guided by the housing 1 to the outside shaft 31 serves to transmit the torque between the hydraulic machine and the environment.
  • the torque generated by the fluid pressure in the hydraulic machine is tapped off via this shaft 31 serving as the output shaft.
  • the internal external gears 3, 4, 5, 6 are driven via this shaft 31, which serves as the drive shaft, in order to achieve delivery of the working fluid.
  • the three other housed in the working chamber 2 outer gears 4,5,6 are arranged along the circumference of the working gear 3. They serve as conveyor gears which, together with the working gear 3, each form a gear pair 40, 50, 60.
  • Each of the pairs of gears formed by a feed gear 4,5,6 and the drive gear 3 is an independent motor or pump unit.
  • each of the three externally toothed conveyor gears 4,5,6 a common combing 41,51,61 with the central working gear 3 on.
  • the combing area of two external gears is that region in which the teeth of the involved gears come into mutual engagement. It essentially corresponds to the overlapping area of the head circles of the involved gears.
  • the working gear 3 and the three conveyor gears 4,5,6 are each arranged individually rotatably mounted in the sub-chambers 23,24,25,26 of the working chamber 2. To see a leakage between the side wall of a sub-chamber 23,24,25,26 and the
  • each external gear 3,4,5,6 is tightly enclosed by a part of the housing inner wall over a substantial part of its circumference.
  • Each pair of gears 40,50,60 has its own inlet channel 42,52,62 and a separate outlet channel 43,53,63, which open respectively on opposite sides of the respective combing 41,51,61 in the working chamber 2.
  • the working fluid under high pressure is fed into the working chamber 2 via the high-pressure-side inlet channel 42, 52, 62.
  • the working fluid transported by the respective conveyor gear and the working gear 3 to the mouth region of the respective discharge channel 43, 53, 63 leaves the working chamber 2 via the low-pressure-side discharge channel 43, 53, 63.
  • the inlet channel 42, 52, 62 is preferably arranged on the front side of the toothed wheels, so that its mouth is formed in the side wall of the working chamber 2. As shown in FIG. 1, an inlet channel 42, 52, 62 is directed toward the associated combing area 41, 51, 61. In contrast to this, the mouth of the associated outflow channel 43, 53, 63 arranged on the side of the combing region 41, 51, 61 opposite the inlet channel 42, 52, 62 is formed in a bottom surface of the working chamber 2. As a result of this arrangement of the discharge channel 43, 53, 63, the side wall in the transition between the first sub-chamber 23 and the conveying gear sub-chambers 24, 25, 26 can be made particularly streamlined.
  • the arrangement of the channels 42,43,52,53,62,63 shown in Figure 1 allows a relatively small mutual distance of the conveyor gears 4,5,6 along the circumference of the working gear 3, since the drain and the inlet channels 42, 43,52,53,62,63 of adjacent conveyor gears 4,5,6 do not interfere with each other. This makes it possible to arrange a relatively high number of conveyor gears along the circumference of the working gear 3. Furthermore, a close arrangement of the conveyor gears allows 4,5,6 on only one side of the working gear 3, a relatively compact machine housing 1 produce.
  • Each channel 42,43,52,53,62,63 is preferably connected to its own arranged on the outside of the housing 1 connection.
  • the serving as inputs or outputs for the working fluid connections are usually designed to be connected to special hydraulic lines.
  • Flow channels 42,43,52,53,62,63 also share a common input and output. As a result, the number of connections required on the machine housing 1 can be reduced.
  • the three conveying gears 4, 5, 6, 6 are preferably arranged substantially uniformly along the circumference of the external gear 3.
  • This uniform arrangement of the conveyor gear wheels 4, 5, 6 enables a more uniform loading of the bearings of the external gear 3, whereby advantageously a calmer and easier running of the external gear 3 and a lesser wear of the loaded parts can be achieved.
  • a uniform distribution of the conveyor gears 4,5,6 along the conspiracy leopardradiquess is not absolutely necessary.
  • the number and the distribution of the conveyor gears 4,5,6 along the circumference of the working gear 3 are adapted to the respective needs.
  • the size or diameter of the gears used may vary. In a machine having a relatively large work gear 3, it is possible to arrange a larger number of relatively small feed gears 4, 5, 6 along the outer circumference of the work gear 3. By contrast, by using relatively large conveyor gears 4, 5, 6 and a working gear 3 having a relatively small diameter, the power of the individual conveyor gears 4, 5, 6 can be increased.
  • the conveyor gears 4, 5, 6 of the circulatory displacement machine shown in FIG. 1 are preferably mounted on a non-rotating shaft 45, 55, 65 by means of an inner bearing.
  • a particularly simple and quick installation of the conveyor gears 4,5,6 allows. This is particularly advantageous if the recirculating displacement machine is converted for a special application and at least one feed gear 4,5,6 is to be inserted into an already existing sub-chamber 24,25,26 or removed from the corresponding sub-chamber 24,25,26 ,
  • assembly of the conveyor gears 4, 5, 6 is also possible with a rotating shaft fixedly connected to the respective conveyor gear 4, 5, 6 (not shown here).
  • the drive gear 3 preferably has a relatively large diameter
  • the drive shaft 31 connected to the axis of the work gear 3 is relatively far away from the high pressure areas arranged on its outer circumference.
  • an additional decoupling of the drive shaft 31 can be achieved by the high pressure areas.
  • the working fluid with the full inlet pressure is prevented from acting on the seal of the drive shaft 31.
  • the conveyor gears 4, 5, 6 of the rotary displacement machine shown in FIG. 1 have teeth with a reduced height.
  • By means of such half-gears it is necessary to reduce the fluid consumption of the rotary displacement machine operated as a geared motor.
  • the rotary displacement machine operated as a geared motor.
  • the teeth of the working gear 3 and the respective conveyor gear 4,5,6 not the entire existing in the interdental spaces of the work gear 3 working fluid is displaced.
  • the working fluid remaining in this residual volume is transported back to the respective inlet channel 42, 52, 62 via the respective combing area 41, 51, 61.
  • the necessary flow rate of the working fluid can be reduced.
  • the circulation displacement machine according to the invention can also be operated as an external gear pump.
  • the two externally toothed gears of a gear pair each form an independent pump unit.
  • the pressure medium on the pressure side (outflow side) is pressed out of the tooth spaces, while the suction pressure (on the supply side) results in the vacuum necessary to draw in the working fluid.
  • the circulation displacement machine according to the invention can be modular.
  • a typical module preferably in each case comprises a conveyor gear wheel.
  • the modules can also comprise a plurality of conveyor gears.
  • modules which have no conveyor gears and corresponding sub-chambers can replace unneeded modules with conveyor gears.
  • a replacement module is designed so that the work gear is tightly enclosed by the housing wall in this area. The replacement modules can prevent turbulence and thus achieve higher efficiencies.
  • any configuration of a machine can be produced. In particular, this allows the number, distribution and
  • the performance of the rotary displacement machine can also be adjusted as required during operation by selectively switching off and on the individual conveyor gears or modules.
  • the shutdown of a conveyor gear can for example take place in that the inlet and the outlet channel of the respective conveyor gear are decoupled from the hydraulic circuit and short-circuited with each other.
  • This is NEN inlet channel of an adjacent conveyor gear in the working chamber 2 supplied and transported from the drive gear 3 to the shut-off conveyor gear working fluid is transported in this case only partially along the circumference of the co-rotating conveyor gear.
  • the other part of the working fluid is forwarded via the newly created bypass connection between the drainage channel and the inlet channel of the respective conveyor gearwheel, without the respective conveyor gear wheel being driven in or being conveyed by this conveyor gearwheel.
  • the selective connection and disconnection of the conveyor gears can in principle also be realized in a rotary displacement machine which has a modular design. In this case, entire modules can be bridged via corresponding bypass lines.
  • FIG. 2 shows the housing 1 of the rotary displacement machine according to the invention.
  • a metal such as e.g. Aluminum, or a metal alloy
  • existing housing block 1 is usually composed of plates together.
  • the trained for receiving the gears working chamber 2 is arranged inside the housing block 1, the trained for receiving the gears working chamber 2 is arranged. It is completely isolated from the environment by the housing 1.
  • the working chamber 2 comprises four contiguous sub-chambers 23, 24, 25, 26, which are preferably designed as cylindrical recesses with circular base surfaces. Each sub-chamber 23,24,25,26 is formed for receiving a respective gear 3,4,5,6.
  • the central recess forms a first sub-chamber 23, which is provided for receiving the central working gear 3. It has a relatively large diameter.
  • each of the three further sub-chambers 24, 25, 26 has its own overlap area 241, 251, 261 with the first sub-chamber 23, which in FIG.
  • a first bore 231 is provided in the center of the bottom surface of the first sub-chamber 23.
  • This bore 231 is designed to receive the axis of the working gear 3 and preferably dimensioned so that they can also accommodate an associated ball bearing in addition to the actual axis.
  • a second bore corresponding to the first bore 231 is provided, which is likewise designed to receive the axis of the working gear 3 (this bore is not shown here).
  • the first bore 231 is preferably formed as a continuous bore and serves to lead out the connected to the axis of the working gear 3 shaft 31 out of the housing 1, the second bore is preferably formed as a blind hole. If the shaft 31 is to be executed on one side only from the housing block 1, the sealing of the shaft 31 can thus be simplified.
  • the channels 42,43,52,53,62,63 lead out of the housing block 1 and are preferably connected to inputs and outputs for the working fluid.
  • the inputs and outputs are formed as attached to the outside of the housing block 1 connections, which are preferably provided for the connection of special hydraulic lines.
  • the channels 42, 52, 62, 43, 53, 63 preferably run in the housing block 1 in such a way that the inlet channel 42, 52, 62 assigned to a specific conveyor gear part chamber 24, 25, 26 and the immediately adjacent outlet channel 43, 53, 63 of a neighboring counselffyradteilfit 26,24,25 do not interfere with each other.
  • each inlet channel 42, 52, 62 extends laterally out of the housing block 1, while the corresponding outlet channel 43, 53, 63 runs preferably obliquely in the housing block 1, at least in its first section.
  • shielding elements 44, 54, 64 can be provided, which provide the associated combing region
  • Such a screen element 44,54,64 preferably has a vertical baffle 441,541,641 for the working fluid.
  • the shield element 44, 54, 64 preferably has a wedge-shaped region 442, 542, 622, which engages between the corresponding subchambers 23, 24, 25, 26 and may extend as far as the intersecting region 241, 251, 261 of these subchambers 23, 24, 25, 26.
  • the wedge-shaped area 442, 542, 622 is preferably adapted to the contour of the respective partial chambers 23, 24, 25, 26.
  • the residual volume remaining in the interdental spaces when the teeth of a gearwheel pair engage each other can be increased by suitable measures.
  • 3 shows a specially designed external gear 8 with half teeth, with the aid of which a corresponding circulation displacement machine can be realized with a higher return volume.
  • Such a half gear is preferably used as a feed gear 4,5,6 in the rotary displacement machine shown in Figure 1.
  • the Half gear 8 has special recesses 81 in the bottom surfaces of the interdental spaces, which are preferably cone-shaped or wedge-shaped. By means of these recesses 81, the remaining volume remaining in the inter-engagement of the teeth of the feed gear and the work gear in the interdental spaces of the feed gear can be significantly increased.
  • an increase in the residual volume formed in the mutual engagement of the teeth in the interdental spaces of the working gear 3 can be increased by means of special depressions 82 in the head regions of the conveying gear 4, 5, 6. Both types of depressions 81, 82 can be realized both jointly and individually. In order to avoid material damage, the recesses 81, 82 should always be designed in such a way that the teeth still have sufficient load capacity.
  • FIGS. 4A and 4B show further exemplary embodiments of the rotary displacement machine according to the invention.
  • the machine shown schematically in FIG. 4A has four conveyor gears 4, 5, 6, 7, which are arranged symmetrically about the central work gear 3.
  • the symmetrical arrangement of the conveyor gears 4,5,6,7 allows a particularly uniform loading of the working gear 3 and the associated bearings.
  • Each of the four conveyor gears 4,5,6,7 forms with the central working gear 3 has its own combing, each associated with an inlet and an outlet channel.
  • the housing 1 of the machine has a contour essentially predetermined by the inner working chamber 3.
  • the resulting housing 1 has a substantially square shape with rounded corners. This form proves to be particularly space-saving. Basically, however, since housing can have any shape.
  • the housing 1 of the rotary displacement machine shown in FIG. 4A has a modular construction.
  • a base module 90 is provided that includes two conveyor gears 5.6 and the associated sub-chambers.
  • two individual modules 91,92, each with a conveyor gear 3,7 and the associated sub-chamber are provided in the upper part of the machine.
  • the channels are provided, which are assigned to the respective conveyor gears 4,5,6,7.
  • the working gear 3 and the associated sub-chamber can be part of the base module 90. Due to the modular construction, it is possible to change the configuration of the machine, and in particular the number and distribution of the feed gears along the circumference of the work gear 3.
  • FIG. 4B Such a changed configuration of the machine is shown in FIG. 4B.
  • a single module 92 which contains a conveyor gear 7 and the corresponding sub-chamber, was replaced by a new module 93 without a feed gear and the associated sub-chamber.
  • the new module 93 is preferably designed so that it closely encloses the work gear 3.
  • turbulence can be prevented, which can be caused by the fact that a conveyor gear only removed from its sub-chamber for the purpose of configuration of the machine, or e.g. is bypassed by means of a bypass.
  • FIG. 5 shows, on the basis of a further exemplary embodiment, the interior of a rotary displacement machine which has three conveyor gears 4, 5, 6 arranged symmetrically about a central drive gear 3.
  • the central drive gear 3 in this case has a smaller diameter than the three outer conveyor gears 4,5,6.
  • a favorable transmission ratio can be achieved, in particular during operation as a motor.
  • in motor operation by using half-gear wheels remaining in the interdental spaces of the work gear 3 remaining volume can be increased.
  • a further increase in the residual volume can also be through appropriate depressions in the interdental spaces and in the tooth tips the individual conveyor gears are 4,5,6 increased. For simplicity, these recesses are shown in Figure 5 only a few teeth of the conveyor gears 4,5,6.
  • corresponding recesses may be provided by which both the residual volume and the pressure medium available attack surface can be increased.
  • a corresponding depression is shown in the figure 5 only between the two teeth of the drive gear 3, which are currently in engagement with the teeth of the first conveyor gear 4.
  • FIG. 6 shows a meshing with a drive gear 3 conveyor gear 8. While the teeth of the drive gear 3, full height, the teeth of the conveyor gear 8 are formed as half-teeth. This is indicated by corresponding pitch circle diameter.
  • the conical or wedge-shaped depressions 81, 82 in the head region of a semi-tooth and in the spaces between the teeth each form a groove extending over the entire width of the conveyor gearwheel 8.
  • two half-teeth are shown in a perspective view.
  • additional working surfaces 83, 84 which serve as a contact surface for the pressure medium, were created by the depressions 81, 82.
  • the two meshing gears 3, 8 can be designed such that two dense surfaces are formed. As a result, the radial seal can be improved, resulting in less leakage.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne une machine volumétrique rotative avec un boîtier (1) et avec une première paire (40) de roues dentées à denture extérieure qui est disposée dans une chambre de travail (2) du boîtier (1) et qui est formée d'une roue dentée de travail (3) et d'une première roue dentée de refoulement (4). La première roue dentée de refoulement (4) présente une première région (41) d'engrènement avec la roue dentée de travail (3). Un premier canal d'alimentation (42) pour un fluide de travail débouche dans la première région d'engrènement (41) dans la chambre de travail (2). Sur le côté de la première région d'engrènement (41) qui est opposé au premier canal d'alimentation (42), un premier canal d'évacuation (43) pour le fluide de travail débouche dans la chambre de travail (2) dans une région proche de la première région d'engrènement (41). Une deuxième roue dentée de refoulement (5) à denture extérieure est disposée dans la chambre de travail (2) à l'écart de la première région d'engrènement (41) ; elle forme avec la roue dentée de travail (3) une deuxième paire (50) de roues dentées à denture extérieure, présentant une deuxième région d'engrènement commune (51). Un deuxième canal d'alimentation (52) pour le fluide de travail débouche dans la deuxième région d'engrènement (51) dans la chambre de travail (2). Sur le côté de la deuxième région d'engrènement (51) qui est opposé au deuxième canal d'alimentation (52), un deuxième canal d'évacuation (53) pour le fluide de travail débouche dans la chambre de travail (2) dans une région proche de la deuxième région d'engrènement (51). Le premier canal d'alimentation (42) communique avec le deuxième canal d'évacuation (53) de telle sorte qu'une partie du fluide de travail pénétrant dans la chambre de travail (2) par le premier canal d'alimentation (42) est transportée par la roue dentée de travail (3) vers le deuxième canal d'évacuation (53).
PCT/EP2007/062657 2006-11-21 2007-11-21 Machine volumétrique rotative WO2008062023A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP06024139.5 2006-11-21
EP06024139.5A EP1925823B1 (fr) 2006-11-21 2006-11-21 Machine à engrenages externes

Publications (1)

Publication Number Publication Date
WO2008062023A1 true WO2008062023A1 (fr) 2008-05-29

Family

ID=38007046

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/062657 WO2008062023A1 (fr) 2006-11-21 2007-11-21 Machine volumétrique rotative

Country Status (2)

Country Link
EP (1) EP1925823B1 (fr)
WO (1) WO2008062023A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11280336B2 (en) 2018-03-29 2022-03-22 Schwäbische Hüttenwerke Automotive GmbH Rotary pump with a lubricant feed connecting a rotor bearing and a radial sealing gap

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2478834C2 (ru) * 2011-03-28 2013-04-10 Сергей Васильевич Стороженко Гидромашина
CN103362731B (zh) * 2012-06-07 2015-06-17 北京航天试验技术研究所 四六型非圆齿轮行星轮系液压马达的配流盘及液压马达

Citations (8)

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DE462251C (de) * 1925-07-17 1928-07-06 Eduard Gerberich Zahnrad-Spinnpumpe fuer die Foerderung von Viskose an Kunstseide-Spinnmaschinen
GB605104A (en) * 1945-12-14 1948-07-15 Keelavite Co Ltd Improvements in or relating to rotary pumps
US2745348A (en) * 1952-06-17 1956-05-15 Visioneering Company Inc Motor or pump
US3981646A (en) * 1973-03-15 1976-09-21 Lucas Aerospace Limited Gear pumps and motors
US4165206A (en) * 1977-01-28 1979-08-21 Micropump Corporation Three gear pump with module construction
DE19849804A1 (de) * 1998-10-29 2000-05-11 Voith Turbo Kg Baureihe für Zahnradpumpen mit unterschiedlicher Förderleistung und Verfahren zur Herstellung der einzelnen Zahnradpumpen der Baureihe
US20020136657A1 (en) * 2001-03-21 2002-09-26 Ewald Dennis G. Center driven pressure clamped hydraulic pump
FR2854220A1 (fr) * 2003-04-24 2004-10-29 Hispano Suiza Sa Roue dentee destinee a une pompe a engrenages et pompe a engrenages munie d'une telle roue

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DE696069C (de) * 1936-12-30 1940-09-26 Joseph Schaefers Pumpenaggregat mit zwei oder mehreren selbstaendigen Zahnradpumpen
US2344628A (en) * 1940-12-26 1944-03-21 Gar Wood Ind Inc Gear pump
US2604051A (en) * 1945-12-14 1952-07-22 Keelavite Co Ltd Rotary pump
GB778523A (en) * 1956-01-18 1957-07-10 Roper Corp Geo D Fluid gear pump or motor
US4204811A (en) * 1977-08-19 1980-05-27 The Garrett Corporation Fluid pumping system

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE462251C (de) * 1925-07-17 1928-07-06 Eduard Gerberich Zahnrad-Spinnpumpe fuer die Foerderung von Viskose an Kunstseide-Spinnmaschinen
GB605104A (en) * 1945-12-14 1948-07-15 Keelavite Co Ltd Improvements in or relating to rotary pumps
US2745348A (en) * 1952-06-17 1956-05-15 Visioneering Company Inc Motor or pump
US3981646A (en) * 1973-03-15 1976-09-21 Lucas Aerospace Limited Gear pumps and motors
US4165206A (en) * 1977-01-28 1979-08-21 Micropump Corporation Three gear pump with module construction
DE19849804A1 (de) * 1998-10-29 2000-05-11 Voith Turbo Kg Baureihe für Zahnradpumpen mit unterschiedlicher Förderleistung und Verfahren zur Herstellung der einzelnen Zahnradpumpen der Baureihe
US20020136657A1 (en) * 2001-03-21 2002-09-26 Ewald Dennis G. Center driven pressure clamped hydraulic pump
FR2854220A1 (fr) * 2003-04-24 2004-10-29 Hispano Suiza Sa Roue dentee destinee a une pompe a engrenages et pompe a engrenages munie d'une telle roue

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11280336B2 (en) 2018-03-29 2022-03-22 Schwäbische Hüttenwerke Automotive GmbH Rotary pump with a lubricant feed connecting a rotor bearing and a radial sealing gap

Also Published As

Publication number Publication date
EP1925823B1 (fr) 2016-08-17
EP1925823A1 (fr) 2008-05-28

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