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
  • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
• • 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
  • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
  • F04C2/084—Toothed wheels
• • 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
  • F04C2230/00—Manufacture
  • F04C2230/60—Assembly methods
• • 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
  • F04C2240/20—Rotors

Definitions

• the invention relates to a series for gear pumps with different
• Delivery rate also a process for the manufacture of the individual gear pumps of the series.
• Hydraulic pumps in the form of gear pumps, in which two meshing gears are used as displacement elements, which run in a housing with close play, are known in a large number of designs. With regard to the type of displacement elements
• hydraulic pump The main characteristic values of the hydraulic pump are the geometric displacement volume and the nominal pressure. Due to the different areas of application and the resulting application requirements, hydraulic pumps are available for different delivery volumes. The offer is usually made in series, with the individual pumps one
• the invention is therefore based on the object of creating a series for gear pumps for different delivery volumes and thus suitability for different application requirements, in which the individual pumps of the series have as many design features as possible and which differ only by slight internal modifications.
• the pumps themselves are to be kept as small as possible with respect to the space required, and the possibility of interchangeability with a pump of larger or smaller delivery volume in hydrostatic systems should be given without the need to replace the entire drive chain.
• a series of gear pumps for different delivery volumes includes at least two pumps. Each pump has at least two meshing gears as displacement or displacement elements. According to the invention it is provided that each Pump of the series has the following design features which are essentially identical in terms of size:
• the different delivery volumes are set according to the invention for pumps in a series with the same center distance between the individual displacement elements and a constant tooth width over the tooth height. It is sufficient if at least one of the two meshing gears is changed in terms of its tip diameter, but both are preferred
• the inventor has recognized that when using so-called high toothing, relatively high delivery volumes can be achieved, since the delivery volume sensitivity is based on the tip diameter or
• Tip circle radius is much higher than with normal gears. Even small changes in the tip circle are sufficient to achieve a corresponding increase in the delivery volume.
• the volume increase in the radial direction of the individual pump in relation to the axes of the displacement elements or the axes of symmetry of the displacement elements is relatively small.
• this statement also applies to a reduction in the tip diameter or tip circle radius of a single displacement element.
• the axial length remains constant for all gear pumps in the series. The only change is in the radial direction, with the volume pump sensitivity being only slightly increased due to the high delivery volume sensitivity over the tip circle radius.
• the constant axial length of the gear pump unit makes it possible to replace the gear pump arranged in a drive chain in accordance with the application requirement for the volume to be pumped by another gear pump of this series, which is designed for larger or smaller pumping volumes, without the entire
• the basic toothing for maximum delivery volume is designed as a high toothing for at least one of the two displacement elements and, for minimal delivery volume, the toothing or the individual tooth elements accordingly on one smaller tip circle diameter are removed or ground.
• the basic unit is designed for maximum delivery volume with regard to the individual meshing gears according to
• the solution according to the invention can be used in gear pumps
• gear pumps are single-flow or multi-flow gear pumps.
• both displacement elements are preferably designed or constructed identically with regard to the size and the toothing geometry, while displacement elements with different designs and dimensions are used in two-flow or multi-flow gear pumps.
• FIG. 1a illustrates a section through a gear pump of a series for gear pumps designed according to the invention and a view II; 1 b1 and 1 b2 illustrate two possible contrasts
• FIGS. 1b1 representing a pump with a larger delivery volume of a series
• FIG. 1b2 with a pump with a smaller delivery volume
• FIGS. 1a and 1b each illustrate a section of the interlocking toothing of the displacement elements of the pumps shown in FIGS. 1a and 1b;
• Fig. 3 shows an application of the solution according to the invention for multi-flow gear pumps with external teeth.
• FIG. 1a1 illustrates a section through a gear pump 1 of a series designed according to the invention for gear pumps for different delivery volumes.
• This has a housing 2 which is delimited at the end by a cover 3.
• the two displacement elements - a first displacement element 4 and a second
• Displacement element 5 - arranged.
• the displacement elements 4 and 5 are designed as externally toothed gears in the form of spur gears which mesh with one another. Both run with tight play in the housing 2.
• the first displacement element 4 is mounted on a drive shaft 6.
• the drive shaft 6 is in turn supported by bearings 7 and 8 in the housing 2 or the cover 3 closing the housing.
• the gear pump 1 also has a pressure connection 8 and a suction connection 9. Both the suction connection 9 and the pressure connection 8 are coupled to corresponding rooms, a so-called pressure chamber 8.1 and a suction chamber 9.1. The one introduced via the drive shaft 6 with the first displacement element 4
• Displacement element the hydraulic fluid is conveyed to the pressure chamber 8 and fed from there to a corresponding consumer or displaced toward it.
• the gear pump 1 with axial play compensation. This can be done by acting on one side of the bearing of the displacement elements or on both sides
• the delivery volume is described according to the invention by the individual teeth of the displacement elements 4 and 5 and the inner wall 10 of the housing 2, i.e. by the so-called tooth gaps 4.1 and 5.1 between two adjacent tooth elements 4A and 4B or 5A and 5B of the individual displacement elements 4 and 5, as shown in FIG. 1a1 in a view l-l corresponding to FIG.
• Both displacement elements 4 and 5 are for the execution according to Fig.
• the axes of rotation or symmetry R1 for the displacement element 4 and R2 for the displacement element 5 are at a certain distance, that is to say the axis distance a in the case shown.
• the extension of the gear pump unit 1 in the axial direction is characterized by the dimension b. 1 b1 and 1 b2 for an embodiment of a gear pump 1 and a further gear pump 100 from the gear pump series according to the invention it can be seen that the distances between the theoretical axes of rotation or axes of symmetry R1 or R2, which is also referred to as center distance a, and the axial extension b for both
• the center distance a which is generally determined by the distance between the axes on which the individual displacement elements are mounted, can also be understood as the distance between two rotating shafts, as is the case when the second displacement element is fixed in terms of rotation with a shaft connected is. At least the first displacement element is connected to the drive shaft in a rotationally fixed manner.
• 1 b2 illustrates an embodiment with reduced delivery volumes compared to the gear pump 1 according to FIG. 1b1.
• the displacement elements 4 and 5 for the gear pump 1 and 104 and 105 for the gear pump 100 are designed as high toothing.
• the tip circle diameter d ⁇ 1 B , d K2B for the displacement elements 104 and 105 is smaller than the tip circle diameter d ⁇ 1 , d K2 of the toothing elements 4A, 4B of the gear pump 1.
• the root circle diameter dF 1B and dF 2B for the individual displacement elements 104, 105 and dF 1 and dF 2 of the displacement elements 4, 5 of the gear pumps 100 and 1 are identical.
• the resulting difference in the form of the tooth height z 1A , z 1B or z 2 thus results in the possible displaceable volume between two adjacent tooth elements 104A, 104B or 4A or 4B and 105A, 105B or 5A, 5B different sizes with the same axial extension and thus toothing width z B1 and z B2 .
• the embodiment shown with two identically designed displacement elements 4, 5 or 104 and 105 represents a particularly preferred embodiment. This makes it possible, starting from a gear pump design with displacement elements 4, 5 according to FIG. 1 b1, by simply machining the displacement elements
• the toothing shown is a spur toothing or spur toothing.
• gears are preferably designed as involute gears.
• toothing of the individual toothing elements in a complementary manner to one another as helical toothing. Such a design is characterized by a very low noise level for large and small
• FIGS. 1b1 and 1b2 illustrate sections from a view from the right of FIGS. 1b1 and 1b2 in an enlarged view. These serve the
• FIG. 2a shows an embodiment corresponding to FIG. 1b1
• FIG. 2b shows an embodiment corresponding to FIG. 1b2.
• the geometric parameters for characterizing a toothing are entered again.
• the base circle diameter d 4 , d 104 , d 5 , d 105 are shown . Furthermore, the tip diameter d ⁇ , d ⁇ 1B and the root diameter d F1 , d F2 , d F1A , d F1B and the tooth heights z v z 2 , z 1B and z 2B .
• the individual displacement elements 4, 5 and 104, 105 for example, have an identical division p.
• the design of the displacement elements of a pump in a pump series with identical dimensions or with an identical geometric design enables a particularly standardized production of the individual pumps of the pump series.
• FIG. 3 illustrates a sectional view of a view from the right of a gear pump 200 with external teeth in the form of a two-flow gear pump in a sectional view.
• This has three displacement elements, a first displacement element 204 and two further displacement elements 205.1 and 205.2. These are arranged and stored in a housing 202 with a housing cover 203, preferably of an axial design.
• the gear pump 200 has two suction connections 209.1 and 209.2 and two pressure connections 208.1 and 208.2. These are each connected to corresponding suction spaces 211.1, 211.2 and pressure spaces 212.1 and 212.2.
• the suction spaces and pressure spaces are formed in the area of the intermeshing displacement elements.
• the displacement element 204 functions as a drive element and is therefore at least indirectly connected in a rotationally fixed manner to a drive shaft 206 or to another device, the displacement element 204 being mounted on an axis by means of a sliding bearing. Via the displacement element 204, the torque is transmitted to the further two displacement elements 205.1 and 205.2, which then rotate about their theoretical axis of rotation R 205. And R 205 2 .
• the two displacement elements 205.1 and 205.2 are either rotatably mounted on a shaft or on an axis.
• the displacement elements are designed with different dimensions. In particular, they differ with regard to their tip circle diameter d ⁇ , the base circle diameter d F and the base circle diameter d.
• the two second displacement elements 205.1 and 205.2 are geometrical
• FIGS. 1 to 3 represent preferred configurations of gear pumps of an invention

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

Applications Claiming Priority (3)

Publications (1)

Family

ID=7885999

Family Applications (1)

Country Status (8)

Families Citing this family (4)

Family Cites Families (10)

• 1998
  • 1998-10-29 DE DE19849804A patent/DE19849804C2/de not_active Withdrawn - After Issue
• 1999
  • 1999-10-18 EP EP99950754A patent/EP1044331A1/de not_active Withdrawn
  • 1999-10-18 CA CA002317013A patent/CA2317013A1/en not_active Abandoned
  • 1999-10-18 KR KR1020007007185A patent/KR20010033665A/ko not_active Application Discontinuation
  • 1999-10-18 US US09/581,645 patent/US6540493B1/en not_active Expired - Fee Related
  • 1999-10-18 JP JP2000579893A patent/JP2002529644A/ja active Pending
  • 1999-10-18 WO PCT/EP1999/007878 patent/WO2000026539A1/de not_active Application Discontinuation
  • 1999-10-18 CZ CZ20002294A patent/CZ20002294A3/cs unknown

Non-Patent Citations (1)

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