EP1925823A1 - Machine à engrenages externes - Google Patents

Machine à engrenages externes Download PDF

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Publication number
EP1925823A1
EP1925823A1 EP20060024139 EP06024139A EP1925823A1 EP 1925823 A1 EP1925823 A1 EP 1925823A1 EP 20060024139 EP20060024139 EP 20060024139 EP 06024139 A EP06024139 A EP 06024139A EP 1925823 A1 EP1925823 A1 EP 1925823A1
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EP
European Patent Office
Prior art keywords
gear
working
displacement machine
rotary displacement
conveyor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP20060024139
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German (de)
English (en)
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EP1925823B1 (fr
Inventor
Johann Sagawe
Gottfried Sagawe
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Individual
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Individual
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Publication date
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Priority to EP06024139.5A priority Critical patent/EP1925823B1/fr
Priority to PCT/EP2007/062657 priority patent/WO2008062023A1/fr
Publication of EP1925823A1 publication Critical patent/EP1925823A1/fr
Application granted granted Critical
Publication of EP1925823B1 publication Critical patent/EP1925823B1/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 thoroughlyenyakradmotor and a hydraulic external gear pump, wherein a central output or 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 gears are typically driven by a pressurized pressure medium (usually a fluid or working fluid) (hydraulic gear motor) or driven by an external drive for pumping the fluid (hydraulic gear pump).
  • the performance of a rotary displacement machine in addition to its design-related operation, in particular determined by the pressure difference between the high pressure and the low pressure zone of the machine. By increasing the pressure or the torque, 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 inlet channel and the second outlet channel are fluidly with each other connected, that in normal operation of the rotary displacement machine, a part of the flowing through the first inlet channel into the working chamber working fluid is transported from the working gear to the second outlet channel.
  • 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 coupling of the hydraulic machines, 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 also only one drive or output shaft must 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 Kämm Scheme.
  • 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 such that a portion of the working fluid flowing into the working chamber through the second inlet channel is transported from the working gear wheel to the third outlet channel.
  • the work gear is formed as a central gear, arranged along the circumference at least three conveyor gears are that 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.
  • the use of such a baffle allows advantageous guidance of the flowing working fluid.
  • a particularly advantageous embodiment of the invention provides that the screen element has a wedge-shaped region which engages between the feed gear and the working gear.
  • 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 in the operation of the machine as a motor have a relation to the teeth of the working gear reduced height, wherein the by the mutual Engagement of the teeth of the conveyor gear and the working gear in the interdental spaces of the working 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 separately switched on and off in order to set a desired power. As a result, the performance of the machine can be adapted without modification of the respective application.
  • 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.
  • four intermeshing external gears 3,4,5,6 are arranged in the working chamber. 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 guided preferably through the housing 1 to the outside shaft 31 is used for transmission 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 pair of gears 40,50,60.
  • Each of the gear pairs 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.
  • the diameter of the preferably circular sub-chambers in Essentially adapted to the tip circle diameters of the respective gears.
  • 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 conveying toothed wheel and the work gear 3 to the mouth region of the respective outlet channel 43, 53, 63 leaves the working chamber 2 via the low-pressure-side outlet 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. By this arrangement of the flow channel 43,53,63, the side wall can be formed in the transition between the first sub-chamber 23 and the conveyor gear sub-chambers 24,25,26 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 adjacent conveyor gears 4,5,6 not disturb 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.
  • several of the inlet or outlet channels 42, 43, 52, 53, 62, 63 running in the housing 1 can also share a common inlet or outlet. 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 gears 4,5,6 allows a more uniform load on the bearings of the external gear 3, which advantageously a quieter and easier running of the external gear 3 and a lower wear of the loaded parts can be achieved.
  • a uniform distribution of the conveyor gears 4,5,6 along the horryingradiquess is not mandatory.
  • 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.
  • 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.
  • 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.
  • gears 3,4,5,6 By providing the same size gears 3,4,5,6 turn the manufacturing cost of the machine can be reduced.
  • the conveyor gears 4, 5, 6 of the rotary 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 ,
  • an assembly of the conveyor gears 4,5,6 with a firmly connected to the respective feed gear 4,5,6 rotating shaft is possible (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 feed gear wheels 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 all of the existing in the interdental spaces of the working 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 drain side
  • the suction side inlet side
  • 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 subchambers 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.
  • it can be used to change the number, distribution and size of the conveyor gears of the machine. This makes it possible to build the machine to the respective power requirements. This allows a flexible use of Umlaufverdrängermaschine invention.
  • the performance of the rotary displacement machine can be adjusted as needed by the individual conveyor gears or modules targeted off or switched on.
  • 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.
  • the working fluid supplied into the working chamber 2 through an inlet channel of an adjacent conveyor gear wheel and transported from the drive gearwheel 3 to the switched-off gearwheel is in this case transported only partially along the circumference of the co-rotating conveying gearwheel.
  • the other part of the working fluid is via the newly created bypass connection forwarded between the drain and the inlet channel of the respective conveyor gear, without driving the respective conveyor gear or be funded by this conveyor gear.
  • the targeted connection and disconnection of the conveyor gears can basically be implemented in a rotary displacement machine, which has a modular design. Whole 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 intersection region 241, 251, 261 with the first sub-chamber 23, which essentially corresponds to the respective combing region 41, 51, 61 formed by the mutual tooth engagement of the associated toothed wheels.
  • 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 led out of the housing block 1 only on one side, so that the sealing of the shaft 31 can be simplified.
  • special holes 42,43,52,53,62,63 are provided, which serve as inlet or outlet channels for the working fluid.
  • the orifices of these channels 42,43,52,53,62,63 are arranged directly in the vicinity of the overlap regions 241,251,261 of the sub-chambers 23,24,25,26, wherein the inlet channels 42,52,62 respectively on the the flow channels 43, 53.63 opposite side of the associated overlap region 241,251,261 open into the working chamber 2.
  • 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 designed as connections attached to the outside of the housing block 1, 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 directly adjacent outlet channel 43, 53, 63 of a adjacent counselffyradteilfit 26,24,25 do not interfere with each other.
  • each inlet channel 42, 52, 62 leads laterally out of the housing block 1 out, while the corresponding outlet channel 43,53,63 preferably extends at least in its first portion obliquely in the housing block 1.
  • shielding elements 44, 54, 64 may be provided, which provide the associated combing region 41, 51, 61 from the respective feed channel 42, 52 , 62 shield.
  • 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, 29, 25, 26.
  • the wedge-shaped area 442, 542, 622 is preferably adapted to the contour of the respective partial chambers 23, 24, 25, 26.
  • FIG. 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.
  • 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.
  • FIGS. 4A and 4B show further exemplary embodiments of the rotary displacement machine according to the invention.
  • the machine shown schematically in Figure 4A four conveyor gears 4,5,6,7, which are arranged symmetrically about the central working 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 in the present example a substantially predetermined by the inner working chamber 3 contour.
  • 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 in the lower part of the machine 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, the respective conveyor gears 4,5,6,7 assigned.
  • 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 includes the work gear 3 closely. As a result, turbulence can be prevented, which can be caused by the fact that a conveyor gear for the purpose of configuration of the machine only removed from its sub-chamber or bypassed for example by means of a bypass.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP06024139.5A 2006-11-21 2006-11-21 Machine à engrenages externes Not-in-force EP1925823B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP06024139.5A EP1925823B1 (fr) 2006-11-21 2006-11-21 Machine à engrenages externes
PCT/EP2007/062657 WO2008062023A1 (fr) 2006-11-21 2007-11-21 Machine volumétrique rotative

Applications Claiming Priority (1)

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

Publications (2)

Publication Number Publication Date
EP1925823A1 true EP1925823A1 (fr) 2008-05-28
EP1925823B1 EP1925823B1 (fr) 2016-08-17

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WO (1) WO2008062023A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012134324A1 (fr) * 2011-03-28 2012-10-04 Storozhenko Sergey Vasilievich Machine hydraulique
CN103362731A (zh) * 2012-06-07 2013-10-23 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
RU218291U1 (ru) * 2022-12-13 2023-05-22 Акционерное общество "Всероссийский научно-исследовательский институт гидротехники имени Б.Е. Веденеева" Комбинированная шестеренная гидромашина

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Publication number Priority date Publication date Assignee Title
DE102018107695A1 (de) 2018-03-29 2019-10-02 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe

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US2344628A (en) * 1940-12-26 1944-03-21 Gar Wood Ind Inc Gear pump
GB605104A (en) * 1945-12-14 1948-07-15 Keelavite Co Ltd Improvements in or relating to rotary pumps
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
DE2830598A1 (de) * 1977-08-19 1979-03-01 Garrett Corp Stroemungsmittelpumpeinrichtung
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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DE462251C (de) * 1925-07-17 1928-07-06 Eduard Gerberich Zahnrad-Spinnpumpe fuer die Foerderung von Viskose an Kunstseide-Spinnmaschinen
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
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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
GB605104A (en) * 1945-12-14 1948-07-15 Keelavite Co Ltd Improvements in or relating to rotary pumps
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
DE2830598A1 (de) * 1977-08-19 1979-03-01 Garrett Corp Stroemungsmittelpumpeinrichtung
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 (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012134324A1 (fr) * 2011-03-28 2012-10-04 Storozhenko Sergey Vasilievich Machine hydraulique
CN103362731A (zh) * 2012-06-07 2013-10-23 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
RU218291U1 (ru) * 2022-12-13 2023-05-22 Акционерное общество "Всероссийский научно-исследовательский институт гидротехники имени Б.Е. Веденеева" Комбинированная шестеренная гидромашина

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