• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Gear pump with intermeshing of a pump housing (2) enclosed gears (1, 1 ') arranged on longitudinal axes (9, 10), each laterally of the gears (1, 1') protruding bearing pin (5, 6), wherein at least one of Bearing journal (5, 6) has at least over part of its axial extent a bearing journal diameter which is in the range of 90% to 100% of a root diameter of the toothing of the associated gear (1, 1 '), characterized in that a tooth width b at least twice is as large as an axial distance a of the longitudinal axes (9, 10), wherein the tooth width b is an extension of the toothed wheels (1, 1 ') parallel to the longitudinal axes (9, 10) that a cross section of a pump inlet in an upper toothing plane ( 24) is square, wherein the upper toothing plane (24) corresponds to a plane just above the toothing of the gears (1, 1 '), and that the suction side, a transition region (25) with a wall is provided (26), as viewed in the conveying direction of a circular inlet cross-section to the pump inlet in the upper toothing plane (24), wherein the transition region (25) has an extension H in the conveying direction of the pumping medium, wherein the extension H is defined as follows: where α is a maximum opening angle of the wall (26) in the transition region (25) and is defined as the maximum angle between the conveying direction of pumping medium and a connecting line, which by the connection from a starting point (A) on the upper toothing plane (24) is given to an end point (B), which indicates an upper end of the wall (26) is given.
    公开号:CH710429B1
    申请号:CH00411/16
    申请日:2013-10-01
    公开日:2016-12-30
    发明作者:Heinen Michael；Triebe René
    申请人:Maag Pump Systems Ag；
    IPC主号:
    专利说明:

    The present invention relates to a gear pump according to the preamble of claim 1 and a use of the gear pump.
    Gear pumps essentially consist of a pair of intermeshing gears which are enclosed by a housing and from which bearing journals arranged laterally around the longitudinal axis protrude, which have their seat in fluid-lubricated slide bearings.
    [0003] Since gear pumps have a characteristic curve that is stiff to conveyance, they are particularly suitable for the transport of conveyed media from a suction to a pressure side. Between the two latter, the volume flow promoted in the downstream units creates a pressure gradient which is particularly large in the case of highly viscous media and which leads to a power transmission to each gearwheel. Since this power transmission results in a load on the bearing formed by the bearing journals and plain bearings, the maximum applicable pressure gradient is limited by the bearing capacity of this bearing, the bearing bearing capacity depending on the strength of the bearing journals and in particular the diameter of the bearing journals.
    A gear pump with maximum bearing capacity is known from EP-1 790 854 A1 of the same applicant. In this known gear pump, the bearing journals have, at least over part of their axial extent, a bearing journal diameter which is in the range of 90% to 100% of a root diameter of the toothing of the associated gear.
    [0005] It is an object of the present invention to further improve the known gear pump, in particular with regard to its filling behavior.
    [0006] This object is achieved by the features listed in the characterizing part of claim 1. Variants of the present invention and a use are specified in further claims.
    The present invention thus initially relates to a gear pump with interlocking gears enclosed by a pump housing with bearing journals arranged on longitudinal axes, each laterally protruding from the gears, at least one of the bearing journals having a journal diameter at least over part of its axial extent which is in the area from 90% to 100% of a root diameter of the toothing of the associated gear. The gear pump according to the invention is characterized in that a toothing width b is at least twice as large as a center distance a of the longitudinal axes, the toothing width b being an extension of the gearwheels parallel to the longitudinal axes, that a cross section of a pump inlet in an upper toothing plane is square, The upper toothing level corresponds to a plane just above the toothing of the gears, and that a transition area with a wall is provided on the suction side which, viewed in the conveying direction, leads from a circular inlet cross-section to the pump inlet in the upper toothing level, the transition area having an extension H in the conveying direction of the Has pump medium, where the extent H is defined as follows:
    where α is a maximum opening angle of the wall in the transition area and is defined as the maximum angle between the conveying direction of the pump medium and a connecting line, which is created by the connection from a starting point, which is on the upper toothing plane, to an end point, which is an upper end of the wall indicates is given.
    A variant of the inventive gear pump is that the toothing width b corresponds at most to twice the center distance a plus six times a tooth height h of the gears.
    Further variants of the inventive gear pump consist in that the tooth width b is in a range whose lower limit corresponds to twice the center distance a and whose upper limit corresponds to twice the center distance a plus twice the tooth height h of the gears.
    Further variants of the inventive gear pump are that the tooth width b is in a range whose lower limit corresponds to twice the center distance a plus twice the tooth height h of the gears and the upper limit corresponds to twice the center distance a plus four times the tooth height h of the gears .
    Further design variants of the gear pump according to the invention consist in that the toothing width b corresponds to twice the center distance a plus three times the tooth height h of the gears.
    Further design variants of the gear pump according to the invention consist in that the maximum opening angle α is in the range from 20 ° to 50 °, preferably equal to 40 °.
    [0013] Further design variants of the gear pump according to the invention consist in that a wall in the transition area runs in a straight line in all cutting planes running through a central axis.
    [0014] Further design variants of the gear pump according to the invention consist in that a wall in the transition area runs piece-wise in a straight line in predetermined cutting planes running through a central axis.
    [0015] Further design variants of the gear pump according to the invention consist in that a wall in the transition area runs piece-wise continuously and / or piece-wise in a straight line in predetermined cutting planes running through a central axis.
    Further design variants of the gear pump according to the invention consist in that tangents running in the sectional planes enclose a maximum angle of ± 10 ° with the respective opening angle α at any point on the piece-wise continuously running wall in the transition area.
    [0017] Finally, the present invention relates to a use of the gear pump according to one or more of the above-mentioned embodiment variants for conveying a highly viscous polymer melt.
    In the following, the present invention is explained further purely by way of example with reference to drawings. 1 shows a known gearwheel with bearing journals in a perspective view, FIG. 2 shows a section through the longitudinal axis of the arrangement according to FIG. 1, FIG. 3 shows a gear pump according to the invention in a plan view and a section perpendicular to the longitudinal axes of the gear pump, and FIG 4 shows a further embodiment variant, shown in detail, of a wall in the transition area between the inlet and the toothing plane in a cross section according to FIG. 3, bottom.
    Fig. 1 shows a gear 1 for a gear pump with teeth 20 and bearing journals 5 and 6, with a second gear with the respective bearing journals as well as the fixed components of the gear pump - such as housing, slide bearings, drive, etc. - for the sake of simplicity are not shown. The bearing journals 5 and 6 have - at least over part of their axial extent - a bearing journal diameter DL which is in the range from 90% to 100% of a root diameter DF of the gear wheel 1. Of course, this also applies to the bearing journals, not shown in FIG. 1, of the second gear.
    The teeth 20 of the gear 1 have tooth faces 22, of which in Fig. 1 only the tooth faces 22 facing the journal 6 can be seen and which have stress-optimized transitions 17 to attenuate the stresses caused by the notch effect. The stress-optimized transitions 17 consist, for example, of one or more tangentially converging radii which extend up to the surface of the bearing journal 6.
    In the example shown in Fig. 1, the journal diameter DL is approximately as large as the root diameter DF.
    Fig. 2 shows a section through tooth gaps of the gear 1 and through a longitudinal axis 9 of the bearing pin 5, 6 or the gear 1. It can be clearly seen that the bearing pin diameter DLin approximately corresponds to the root diameter DF, so that on the bearing pin 6 facing surface of the gear wheel 1 essentially only the tooth end faces 22 are exposed.
    Fig. 3 shows a pump inlet on the suction side in a plan view (upper half of Fig. 3) and a cross section through the gear pump perpendicular to the longitudinal axes 9 and 10 (lower half of Fig. 3).
    In cross section (lower half of Fig. 3) are the two gears 1 and 1 ', a pump housing 2, which receives the gears 1, 1' and the pins 5, 6 (Fig. 1), and an inlet 23 evident. The inlet 23 can be in the form of a tube leading to a reactor vessel, or the reactor vessel itself, which has, for example, conical walls. In Fig. 3, such an inlet 23 'running conically at an inlet angle β is indicated by dashed lines. The height of the pump inlet is denoted by H, which corresponds to the distance from a plane just above the toothing of the gears 1, 1 '(hereinafter referred to as the upper toothing plane 24) and the lower end of the inlet 23. This pump inlet is a transition area 25 belonging to the gear pump or its housing, with a wall 26 from a circular cross section of the inlet 23 to a rectangular cross section of the upper toothing plane 24. In the cross section shown in the lower half of FIG. 3, the wall 26 of the Transition area 25 further characterized by a point A, which lies on the toothing plane 24, and a point B, which characterizes the upper end of the wall 26.
    In principle, in further embodiment variants of the present invention, it is conceivable that the cross section of the inlet 23 deviates from a circular cross section and / or that the cross section on the upper toothing plane 24 deviates from a rectangular cross section.
    The transition region 25 - and thus the wall 26 - has, again with a view to the embodiment according to FIG. 3, starting from the rectangular cross-section of the upper toothing plane 24 (ie from point A) to a maximum opening angle α, from which the Height H is dependent, the height H increasing when the maximum opening angle α is reduced. The opening angle α corresponds to the angle between the central axis M and the connection of the points A and B.
    When using the gear pump for pumping highly viscous polymer melts from a reactor, it is of the greatest importance that the lowest possible inlet pressure loss - also called NPSH - is achieved. This is achieved when the mentioned transition area 25 or the wall 26 between the upper toothing plane 24 and the end area of the inlet 23 is as simple and uniform as possible. In particular, the simple and uniform transition possible without further transitions and edges from the circular reactor cross-section or the circular inlet 23 to the rectangular cross-section should take place directly above the toothing (i.e. the upper toothing plane 24).
    If the cross section of the pump inlet in the upper toothing plane 24 is selected to be as square as possible, preferably square, the condition of an advantageous transition from the circular reactor cross section or the circular inlet 23 to the rectangular cross section on the upper toothing plane 24 is met in the best possible way.
    It has been shown that a first variant of the gear pump according to the invention is obtained when the toothing width b is at least twice as large as an axis distance a of the axes 9 and 10, the toothing width b being an extension of the gears 1, 1 ' is parallel to axes 9 and 10.
    On the other hand, in a further embodiment, the toothing width b is limited by a maximum resulting from twice the center distance a plus six times a tooth height h of the gears 1, 1 '.
    Further design variants I, II and III result from the following information for areas in which the toothing width b lies, namely:
    [0032] Design variant I:
    Design variant II:
    Design variant III:
    The embodiment III is shown in FIG. 3, the inlet cross-section in the upper toothing plane 24 then exactly corresponding to a square when its corners are in alignment with the inner diameter DE of the inlet 23.
    If now, as proposed in a further embodiment of the present invention, the maximum opening angle α in the range of 20 ° to 50 °, in particular equal to 40 °, is selected, the height H of the transition area is reduced as a function of the maximum opening angle α and the tooth width b as follows:
    This means that the height H of the transition area with a constant maximum opening angle α is directly proportional to the toothing width b. In an embodiment of the present invention in the sense of the above explanations for height H, not only is an extremely low inlet pressure loss (NPSH) obtained, but also a short transition area 25, which increases the overall height of the entire assembly, consisting of gear pump and reactor vessel is optimized to a minimum.
    From Fig. 3, below, it can be seen that there is a straight connection between points A and B, as is provided in an embodiment of the present invention. In a modification of this straight course of the wall 26 in the transition area 25, it is conceivable in further embodiment variants of the present invention that the position of the two points A and B as connection points (starting point and end point) remain the same, whereas the course between these points A and B in one can run arbitrarily to a certain extent. For example, it is provided in further design variants that the course of the wall 26 is only piecewise in a straight line between points A and B. 4 shows a possible embodiment variant in which the connection between points A and B is again defined by the opening angle α, but the actual course of the wall 26 takes place via a point C, which lies between points A and B. The actual course of the wall 26 deviates at point A from the connecting line between points A and B by an angle δ and at point B from the connecting line between points B and A by angle γ. This results in a piece-wise straight course of the wall 26 over the point C.
    The two angles γ and δ can be within an angular range of ± 10 °, preferably within an angular range of ± 5 °, whereby it is not necessary that both angles γ and δ are equal. Rather, the individual values of the angles γ and δ are chosen in such a way that point C is at a suitable point.In principle, however, it is also not necessary for the connection between points A and B - and thus the wall 26 - to run piece by piece in a straight line. Rather, a continuously curved line between points A and B or a continuously curved line in sections in combination with piece-wise straight sections is also conceivable, with a tangent at any point on the curved line, the above-mentioned criteria for the angular magnitude γ and δ between the Tangent and the straight connecting line between points A and B should also meet.
    A possible reason for a deviation from a straight connection between points A and B is, for example, a heating bore 30 (FIG. 4) for the liquid temperature control in the inlet 23.
    As can be seen from Fig. 3, above, the angle α in the section plane shown (Fig. 3, below) and a section plane perpendicular to this is greatest for the same variant. If a section plane is considered which deviates from the section planes mentioned (the section plane shown in FIG. 3, above, and the section plane running perpendicular to it), the opening angle α is smaller in such deviating section planes. If the cutting plane is laid through point D, the opening angle α is equal to zero. For this reason, the opening angle α is always a maximum angle which, in a specific embodiment variant, occurs in the sectional plane shown in FIG. 3 - or perpendicular to it.
    权利要求:
    Claims (11)
    [1]
    1. Gear pump with interlocking gears (1, 1 ') enclosed by a pump housing (2) with bearing journals (5, 6) arranged on longitudinal axes (9, 10) and protruding laterally from the gears (1, 1'), whereby at least one of the bearing journals (5, 6) has at least part of its axial extension a bearing journal diameter (DL) which is in the range of 90% to 100% of a root diameter (DF) of the toothing of the associated gearwheel (1, 1 '), thereby characterized in that a toothing width b is at least twice as large as a center distance a of the longitudinal axes (9, 10), the toothing width b being an extension of the gear wheels (1, 1 ') parallel to the longitudinal axes (9, 10), that a Cross-section of a pump inlet in an upper toothing plane (24) is square, the upper toothing plane (24) corresponding to a plane just above the toothing of the gears (1, 1 '), and that on the suction side a transition area (25) with a wall (26) is provided which, viewed in the conveying direction, leads from a circular inlet cross-section to the pump inlet in the upper toothing plane (24), the transition region (25) having an extension H in the conveying direction of the pump medium, the extension H being defined as follows:
    where α is a maximum opening angle of the wall (26) in the transition area (25) and is defined as the maximum angle between the conveying direction of the pump medium and a connecting line, which is formed by the connection of a starting point (A) on the upper toothing plane (24) is to an end point (B), which characterizes an upper end of the wall (26) is given.
    [2]
    2. Gear pump according to claim 1, characterized in that the toothing width b corresponds at most to twice the center distance a plus six times a tooth height h of the gears (1, 1 ').
    [3]
    3. Gear pump according to claim 1 or 2, characterized in that the toothing width b is in a range whose lower limit corresponds to twice the center distance a and whose upper limit corresponds to twice the center distance a plus twice the tooth height h of the gears (1, 1 ') .
    [4]
    4. Gear pump according to claim 1 or 2, characterized in that the toothing width b is in a range, the lower limit of which is twice the center distance a plus twice the tooth height h of the gears (1, 1 ') and its upper limit is twice the center distance a plus corresponds to four times the tooth height h of the gears (1, 1 ́).
    [5]
    5. Gear pump according to one of claims 1, 2 or 4, characterized in that the toothing width b corresponds to twice the center distance a plus three times the tooth height h of the gears (1, 1 ').
    [6]
    6. Gear pump according to one of claims 1 to 5, characterized in that the maximum opening angle α is in the range from 20 ° to 50 °, preferably equal to 40 °.
    [7]
    7. Gear pump according to one of the preceding claims, characterized in that the wall (26) in the transition region (25) extends in a straight line in all cutting planes extending through a central axis (M).
    [8]
    8. Gear pump according to one of claims 1 to 6, characterized in that the wall (26) in the transition region (25) runs piece-wise in a straight line in predetermined cutting planes extending through a central axis (M).
    [9]
    9. Gear pump according to one of claims 1 to 6, characterized in that the wall (26) in the transition region (25) runs piece-wise continuously and / or piece-wise in a straight line in predetermined cutting planes running through a central axis (M).
    [10]
    10. Gear pump according to claim 9, characterized in that tangents running in the sectional planes enclose a maximum angle of ± 10 ° with the respective opening angle α at any point of the piece-wise continuously extending wall in the transition region (25).
    [11]
    11. Use of the gear pump according to one of claims 1 to 10 for conveying a highly viscous polymer melt.
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    同族专利:
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    引用文献:
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    PCT/EP2013/070394|WO2015048984A1|2013-10-01|2013-10-01|Gear pump with improved pump inlet|
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