EP1925822A1 - Machine à engrenages externes - Google Patents

Machine à engrenages externes Download PDF

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Publication number
EP1925822A1
EP1925822A1 EP06024138A EP06024138A EP1925822A1 EP 1925822 A1 EP1925822 A1 EP 1925822A1 EP 06024138 A EP06024138 A EP 06024138A EP 06024138 A EP06024138 A EP 06024138A EP 1925822 A1 EP1925822 A1 EP 1925822A1
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EP
European Patent Office
Prior art keywords
working
gear
chamber
fluid
channel
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.)
Withdrawn
Application number
EP06024138A
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German (de)
English (en)
Inventor
Johann Sagawe
Gottfried Sagawe
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
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Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to EP06024138A priority Critical patent/EP1925822A1/fr
Publication of EP1925822A1 publication Critical patent/EP1925822A1/fr
Withdrawn legal-status Critical Current

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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
    • F04C2/12—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

Definitions

  • the invention relates to a rotary displacement machine, in particular a hydraulic external gear motor or an external gear pump with a decoupled from the pressure range drive or driven gear.
  • 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.
  • a suitable working fluid driven (hydraulic gear motor) or driven to promote the fluid via an external drive (hydraulic gear pump).
  • a geared motor the rotational movement of the gears generated by means of a pressure gradient of the working fluid is typically tapped via an output shaft in communication with the rotating gears.
  • the gears are rotated by the drive shaft in communication with the rotating gears to generate a pressure difference of the hydraulic fluid.
  • a typical rotary displacement machine consists of two externally toothed gears whose teeth mesh with each other.
  • the drive or the output is typically carried out via a shaft connected to the axis of one of the two gears.
  • the shaft inside the housing is exposed to the pressure prevailing in the high-pressure zone.
  • the working fluid can escape from the machine housing via the outlet opening of the shaft.
  • very elaborate sealing measures of the drive or output shaft are usually necessary.
  • a separate connected to the shaft drive / driven gear is already provided, which itself is not involved in the promotion of the fluid, but only causes a torque transmission between the shaft and the conveyor gears.
  • the additional drive / driven gear is arranged in the low pressure region of the working chamber. Since this gear is not directly exposed to the fluid under high pressure, no complex sealing measures of the shaft are necessary. The seal can therefore be done with relatively simple measures.
  • a gear machine with two meshing conveyor gears and an additional drive gear is eg from the DE 199 40 730 A1 known. Since the drive of the machine operating as an external gear pump takes place via the drive wheel decoupled from the high-pressure region, a relatively simple and inexpensive seal is sufficient for the drive shaft.
  • the recirculating displacement machine disclosed in this document is operated only as a hydraulic pump. Due to its special design, the operation of this machine as a gear motor is not possible.
  • a recirculating displacement machine which has a housing and three outer gears meshing with each other in a working chamber of the housing.
  • a first and a second external gear which together form a first combing area, as conveyor gears configured to transport a working fluid between a high pressure and a low pressure zone of the working chamber.
  • a third external gear which forms a second combing area in the low-pressure zone of the working chamber with the second conveying gear, is designed as a working gear connected to a shaft.
  • a first channel for the working fluid opens into the high-pressure zone of the working chamber
  • a second channel for the working fluid opens into the low-pressure zone of the working chamber.
  • the work gear is configured to seal the fluid chamber and the second channel from each other. Due to the special arrangement of the working gear in the low pressure zone ensures that the drive shaft is not exposed to high fluid pressure. Thus, a simple sealing of the shaft is possible. At the same time is achieved by the special design of the working gear that the fluid chamber formed between the working gear and the two conveyor gears and the second channel are separated from each other fluidly. This prevents the working fluid between the fluid chamber and the second channel to flow and thereby cause turbulence, which would adversely affect the efficiency of the machine.
  • the working fluid can be transported only in the interdental spaces of the working gear. Due to the existing between the fluid chamber and the second channel pressure difference can be done on the working gear of a gear motor in addition a hydrostatic power conversion by the transported working fluid, so that the working gear is also driven itself. In operation as a gear pump, however, the working fluid is also promoted by the gears of the working gear. In both cases it is possible to prevent turbulence, which depends on the Flow rate of the working fluid and the geometry of the respective flow channels in the working chamber can occur. As far as the working gear is involved in the promotion of the working fluid, the load of the mutually engaged teeth of the participating gears decreases. This can lead to a higher life expectancy or to a higher performance of the machine. Since the load of the bearing of the work gear is better distributed, thus also a smoother running of the gears can be achieved.
  • the working gear over a part of its circumference with the side wall of the working chamber seals tight and thus seals the fluid chamber and the second channel from each other. This ensures that the working fluid can be transported over the part of the circumference of the working gear, which closes tightly with the side wall of the working chamber, only in the interdental spaces of the working gear.
  • a sealing of the fluid chamber from the second channel can be achieved particularly easily.
  • the working gear and the first conveyor gear are coordinated so that the working fluid volume, which is transported by one of these gears into the fluid chamber, transported substantially completely from the other gear out of the fluid chamber becomes.
  • a further advantageous embodiment of the invention provides that each channel opens directed to the associated combing in the working chamber. As a result of this arrangement of the channel, turbulence arising in the working chamber can be reduced, so that in this way the flow in the mouth region of the channels can be favorably influenced.
  • a channel extends substantially perpendicular to a connecting path between the axes of rotation of the respective combing region forming gears. This constructive measure also allows troublesome turbulence in the mouth region of the channels to be further minimized.
  • a particularly advantageous embodiment of the invention provides that the fluid chamber has a discharge channel. This represents a particularly advantageous and simple way by which the maximum pressure occurring during operation of the Umlaufverdrängermaschine may be reduced in the fluid chamber pressure maxima.
  • the relief channel connects the fluid chamber to the second channel.
  • the discharge channel is formed as a groove in a bottom surface of the working chamber.
  • Such a discharge channel can be produced in a particularly simple and cost-effective manner.
  • such a channel can be combined with other channels, which are responsible for example for the lubrication of the gears.
  • the discharge channel has a pressure relief valve.
  • the pressure relief valve arranged in the discharge channel thus allows a low pressure to build up in the fluid chamber. At the same time, it is ensured that the fluid chamber pressure does not exceed the maximum permissible value.
  • a pressure relief valve allows a particularly simple control of the fluid chamber pressure.
  • a further advantageous embodiment of the invention provides that the fluid chamber is limited on the opposite side of the second conveyor gear from a side wall of the working chamber, which has a curvature.
  • the camber can reduce turbulence of the working fluid in the fluid chamber.
  • the flow within the fluid chamber can be favorably influenced.
  • the in the FIG. 1 shown Umlaufverdrängermaschine has a housing 1 with a working chamber 2.
  • the working chamber 2 is completely enclosed by the preferably metallic housing 1 and thereby sealed from the environment.
  • three externally toothed gears 3,4,5 are arranged, the teeth meshing with each other are engaged.
  • the gears 3,4,5 are preferably by means of appropriate bearings, such as sliding or rolling bearings, rotatable in the housing 1 of the hydraulic machine stored.
  • the aasgesenten preferably as ball bearings are in the FIG. 1 partially indicated only.
  • Two external gears 4,5 are designed as conveyor gears.
  • the first and second feed gears 4, 5 are arranged such that their teeth mesh with each other.
  • the two conveyor gears 4, 5 form a first combing area 6.
  • the special arrangement of the two conveyor gears 4, 5 in the machine housing 1 divides the working chamber 2 into a high pressure zone and a low pressure zone I, II.
  • the bainstattradstand is formed a suitable working fluid to transport between the high pressure and the low pressure zone I, II.
  • the conveyor gears are 4.5 tightly enclosed by the side wall of the working chamber 2. This ensures that the working fluid is taken in an opposite direction rotation of the two conveyor gears 4.5 of the teeth of the conveyor gears 4,5 and transported in their interdental spaces.
  • the third external gear 3 forms a special working gear, which is connected to a shaft 31.
  • the shaft 31 is preferably led out of the housing 1.
  • the working gear 3, which serves as a drive (gear pump) or driven gear (gear motor) depending on the operation of the machine, is arranged in the low-pressure zone II and forms with the second conveyor gear 5 a second combing area 7.
  • This combing area 7 is in the gear motor operated machine transmit the torque of the conveyor gears 4,5 on the output gear 3 and the output shaft 31 connected thereto.
  • gear pump gear
  • driven gear driven gear
  • the drive / output shaft 31 is largely decoupled from both in the gear motor and the gear pump of the working fluid under high pressure in the high pressure zone I. As a result, the sealing of the shaft 31 without the usually necessary effort done.
  • the circulation displacement machine according to the invention has two channels 6, 7, via which the working fluid, depending on the operating mode, is fed into the working chamber 2 or removed from the working chamber 2.
  • the first channel 21 preferably opens directly into the working chamber 2 at the edge of the first combing area 6.
  • the mouth of the second channel 22 is located directly in the low-pressure zone II at the edge of the second combing area 7.
  • the working fluid passes into the working chamber 2 via the first channel 21, which serves as the inlet channel, and is subsequently removed from the working chamber 2 via the second channel 22 serving as a discharge channel.
  • the working fluid is sucked in via the second channel 22 and conveyed out of the working chamber 2 via the first channel 21. It is advantageous to arrange the channels 21, 22 essentially perpendicular to a connection path between the axes of rotation of the toothed wheels 3, 4, 5 forming the respective combing region 6, 7. In this way, a favorable flow of the working fluid in the mouth regions of the channels 21,22 can be achieved.
  • both channels 21,22 are substantially perpendicular to the connecting path of the axes of rotation of the respective gears 3,4,5. Due to the almost rectangular To each other arranged gears 3,4,5 and the two channels 21,22 are arranged substantially at right angles to each other. However, the arrangement of the channels 21, 22 does not necessarily have to be rectangular. It depends primarily on the angle at which the three gears are arranged 3,4,5 to each other. In particular, by relatively small angle between the two channels 21,22, the space requirement of Umlaufverdrängermaschine compared to a conventional design can be reduced because the hydraulic connections can then be arranged only on one side of the housing.
  • a fluid chamber 23 is formed, which is arranged on the second channel 22 opposite side of the second combing region 7 in the low pressure zone II of the working chamber 2.
  • the fluid chamber 23 delimited by the working gear 3, the two conveying gears 4, 5 and a side wall of the working chamber 2 forms a fluidic connection between the first conveying gear 4 and the first combing region 6 and the working gear 3.
  • This fluidic connection enables the fluid motor to be used as a gear motor operated by the first conveying gear 4 from the mouth region of the first channel 21 into the fluid chamber 23 transported working fluid can flow directly to the working gear 3 to be transported in the interdental spaces of the working gear 3 to the mouth region of the second channel 22 on.
  • the working fluid carried by the work gear 3 from the mouth portion of the second passage 22 into the fluid chamber 23 can flow directly to the first feed gear 4 via the fluid chamber 23 to continue in the interdental spaces of the work gear 3 to the mouth portion of the first passage 6 to be transported. It is advantageous if the fluid chamber 23 delimiting side wall 27 of the working chamber 2 has rounded edges. This allows a favorable flow resistance for between the first conveyor gear 4 and the working gear. 3 flowing working fluid can be achieved. Such a round curvature 270 of the sidewall is in the FIG. 1 shown.
  • the sealing of the two fluid spaces 22, 23 is preferably achieved by exact adaptation of the corresponding side wall 26 of the working chamber 2 to the work gear 3.
  • the housing 1 surrounds the rotatably mounted work gear 3 so precisely that the gap remaining between the tooth tips of the work gear 2 and the housing 1 can be considered substantially fluidic tight under the operating conditions of the rotary displacement machine. Due to the tight seal between the housing 1 and the side wall 26 of the working chamber 2 and the working gear 3, the working fluid can be transported only in the interdental spaces of the working gear 3 between the second channel 22 and the fluid chamber 23. It is important to emphasize that the maximum gap thickness between the side wall 26 of the working chamber 2 and the working gear 3 is determined in particular by the operating conditions of the rotary displacement machine.
  • a relatively large gap may under certain circumstances also be considered fluidly tight, provided that the leakage across the gap between the working chamber side wall 26 and the working gear 3 is negligibly small compared to the working fluid quantity conveyed in the interdental spaces of the working gear 3.
  • a pressure difference between the fluid chamber 23 and the mouth region of the second channel 22 forms during operation.
  • the absolute pressure in the fluid chamber 22 may not be too high in order to prevent leakage at the outlet opening of the shaft 31.
  • such a pressure difference can also be formed automatically if a portion of the working fluid can flow through the existing gap between the conveyor gears 4, 5 and the housing inner wall during operation of the rotary displacement machine due to the high pressure difference between the high-pressure zone I and the fluid chamber 22.
  • such a pressure difference may also occur relatively quickly, e.g. due to fluctuations in the hydraulic system.
  • the difference in pressure between the fluid chamber 23 and the second channel 22 in operation of the rotary displacement machine as a gear motor causes the drive gear 3 to also undergo hydrostatic power conversion, so that the working gear 3 is driven by the working fluid, albeit to a relatively small extent. Since the pressure difference between the orifice area of the second channel 22 and the fluid chamber 23 is slightly lower than the pressure difference between the mouth areas of the second and first channels 22,21, the hydrostatic power conversion of the first conveyor gear 4 also fell slightly smaller than the hydrostatic power conversion of the second Conveyor gear 5 off. As a result, a lower torque is transmitted to the second conveyor gear 5 via the first combing area 6. Consequently, the torque transmitted from the second feed gear 5 via the second combing region 7 to the work gear 3 is also reduced.
  • the working gear 3 In the operation of the machine as a gear pump, the working gear 3 at an existing pressure difference between the fluid chamber 23 and the mouth region of the second channel 22nd Apply labor to promote the fluid from the suction area in the fluid chamber 23. Due to the existing smaller difference between the fluid chamber 23 and the mouth region of the first channel 21, the first delivery gear 41 must spend less work to convey the working fluid from the fluid chamber 23 to the mouth region of the first channel 21. As a result, the working gear 3 transmits a lower torque to the second conveying gear 5 via the second combing region 71, which in turn transmits a lower torque via the first combing region 6 to the second conveying gear 5.
  • the delivery capacity of the first conveyor gear 4 and the working gear 3 must be precisely matched to each other. In particular, it must be ensured that the delivery chambers formed by the interdental spaces of the two gearwheels 3,4 can accommodate substantially the same volume of fluid.
  • the pressure in the fluid chamber 23 may change in the short term or permanently.
  • a high fluid chamber pressure for the sealing of the drive shaft 31 and thus also for the operation of the Umlaufverdrängerkaschine may have, it must be ensured that the fluid chamber pressure during operation of the machine relative stays low. This can be achieved by a special regulation of the fluid chamber pressure.
  • Such regulation can be realized, for example, by means of a relief channel connecting the fluid chamber 23 to a region of lower pressure.
  • the relief channel 24 is preferably formed between the fluid chamber 23 and the second channel 22. It is advantageous to form the discharge channel 24 as a groove in the bottom surface of the working chamber 2. Such a groove 24 can be made particularly simple. Furthermore, it is also possible in this case to combine the discharge channel 24 with further grooves, which are responsible, for example, for the lubrication of the gears.
  • a pressure relief valve may further be provided in the relief channel 24 (not shown here).
  • the pressure relief valve is preferably designed so that it opens only from the predetermined maximum pressure. Due to the design of the relief channel 24 and the provision of a pressure relief valve, the pressure conditions within the fluid chamber 23 can be controlled very well. In this case, it can also be ensured by a corresponding dimensioning of the relief channel 24 that substantially the same low pressure prevails in the fluid chamber 23 and in the second channel 22. In this case, the working gear 3 transports the working fluid without being driven by itself or without promoting the working fluid thereby.
  • the rotary displacement machine has a housing 1, which is preferably formed from a metal, such as aluminum, or a metal alloy.
  • the working chamber 2 is formed in the interior of the generally composed of plates housing block 1, the working chamber 2 is formed.
  • the FIG. 2 shows a cross section through the housing block 1 of the machine with the inner working chamber 2.
  • the working chamber 2 comprises three sub-chambers for receiving a respective gear 3,4,5.
  • a bore 251,252,253 in the bottom surface 25 is provided in the middle of each sub-chamber.
  • the holes are dimensioned so that they can accommodate the axis of the associated gear and possibly also the respective ball bearing.
  • the holes 252,253 are formed as blind holes. Only the space provided for receiving the working gear 3 partial chamber has at least one through hole 251 in the bottom surface 25, which serves as an outlet opening for the shaft 31.
  • housing has a substantially symmetrical structure.
  • an asymmetrical working chamber 2 and thus an asymmetrical housing 1 is possible when using gears of different sizes.
  • different design of the mouth areas of the first and second channel 22,23 is not mandatory. By means of the curvature, by which the mouth region of the first channel 22 is increased, in particular the flow of the working fluid can be favorably influenced.
  • the housing 1 has a projecting into the working chamber 2 wedge-shaped part 10.
  • the flattened front region of this housing part 10 forms a side wall 27 bounding the fluid chamber 23.
  • the edges of this front region are preferably rounded, whereby a streamlined curvature of the side wall 27 bordering the fluid chamber 23 is formed. As a result, turbulence of the working fluid in the fluid chamber 23 can be reduced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP06024138A 2006-11-21 2006-11-21 Machine à engrenages externes Withdrawn EP1925822A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP06024138A EP1925822A1 (fr) 2006-11-21 2006-11-21 Machine à engrenages externes

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP06024138A EP1925822A1 (fr) 2006-11-21 2006-11-21 Machine à engrenages externes

Publications (1)

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EP1925822A1 true EP1925822A1 (fr) 2008-05-28

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EP06024138A Withdrawn EP1925822A1 (fr) 2006-11-21 2006-11-21 Machine à engrenages externes

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009051443A1 (de) * 2009-10-30 2011-05-05 Storz Endoskop Produktions Gmbh Medizinische Zahnradpumpe
NL2007299C2 (nl) * 2011-05-20 2012-11-21 J G M Van Heck Beheer B V Pomp, pompsysteem en werkwijze voor het verpompen van medium.
CN106968942A (zh) * 2017-06-02 2017-07-21 武汉仁先机械设备有限公司 一种螺杆钻具马达或螺杆泵
DE102017108484A1 (de) * 2017-04-21 2018-10-25 Eberhard Kist Umlaufverdrängermaschine

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1664745A (en) 1926-07-27 1928-04-03 Pratt & Whitney Co Fluid pump
CH172158A (fr) * 1934-03-09 1934-09-30 Tavannes Watch Co Sa Pompe à engrenages.
DE4310211A1 (de) * 1993-03-29 1994-03-24 Bosch Gmbh Robert Hydraulische Zahnradmaschine (Pumpe oder Motor)
DE19940730A1 (de) 1999-08-27 2001-03-01 Johann Sagawe Außenzahnradpumpe

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1664745A (en) 1926-07-27 1928-04-03 Pratt & Whitney Co Fluid pump
CH172158A (fr) * 1934-03-09 1934-09-30 Tavannes Watch Co Sa Pompe à engrenages.
DE4310211A1 (de) * 1993-03-29 1994-03-24 Bosch Gmbh Robert Hydraulische Zahnradmaschine (Pumpe oder Motor)
DE19940730A1 (de) 1999-08-27 2001-03-01 Johann Sagawe Außenzahnradpumpe

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009051443A1 (de) * 2009-10-30 2011-05-05 Storz Endoskop Produktions Gmbh Medizinische Zahnradpumpe
NL2007299C2 (nl) * 2011-05-20 2012-11-21 J G M Van Heck Beheer B V Pomp, pompsysteem en werkwijze voor het verpompen van medium.
WO2012161574A1 (fr) * 2011-05-20 2012-11-29 J.G.M. Van Heck Beheer B.V. Pompe, système de pompe et un procédé de pompage d'une substance
CN103547807A (zh) * 2011-05-20 2014-01-29 吉格姆凡赫克比希尔公司 用于抽吸介质的泵、泵系统及方法
US9587637B2 (en) 2011-05-20 2017-03-07 J.G.M. Van Heck Beheer B.V. Pump, pump system and method for pumping a medium
DE102017108484A1 (de) * 2017-04-21 2018-10-25 Eberhard Kist Umlaufverdrängermaschine
CN106968942A (zh) * 2017-06-02 2017-07-21 武汉仁先机械设备有限公司 一种螺杆钻具马达或螺杆泵

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