EP4170127B1 - Pompe à engrenage - Google Patents

Pompe à engrenage Download PDF

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Publication number
EP4170127B1
EP4170127B1 EP21204258.4A EP21204258A EP4170127B1 EP 4170127 B1 EP4170127 B1 EP 4170127B1 EP 21204258 A EP21204258 A EP 21204258A EP 4170127 B1 EP4170127 B1 EP 4170127B1
Authority
EP
European Patent Office
Prior art keywords
drive unit
connection
designed
unit
connecting elements
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.)
Active
Application number
EP21204258.4A
Other languages
German (de)
English (en)
Other versions
EP4170127A1 (fr
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.)
A&K Mueller GmbH and Co KG
Original Assignee
A&K Mueller GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by A&K Mueller GmbH and Co KG filed Critical A&K Mueller GmbH and Co KG
Priority to DK21204258.4T priority Critical patent/DK4170127T3/da
Priority to EP21204258.4A priority patent/EP4170127B1/fr
Priority to ES21204258T priority patent/ES2994854T3/es
Publication of EP4170127A1 publication Critical patent/EP4170127A1/fr
Application granted granted Critical
Publication of EP4170127B1 publication Critical patent/EP4170127B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/007—General arrangements of parts; Frames and supporting elements
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/604—Mounting devices for pumps or compressors
    • 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
    • F04C2230/70—Disassembly 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
    • F04C2230/00—Manufacture
    • F04C2230/85—Methods for improvement by repair or exchange of parts
    • 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
    • F04C2240/30—Casings or housings
    • 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
    • F04C2240/80—Other components
    • F04C2240/805—Fastening means, e.g. bolts

Definitions

  • the invention relates to a gear pump for conveying a fluid with a conveying unit having at least two gears and a drive unit driving the gears, which are detachably connected to one another via tool-free connecting elements according to claim 1. Further objects of the invention are a pump arrangement with such a gear pump and at least one valve unit and a method for tool-free, detachable connection of the conveying unit and the drive unit of such a gear pump.
  • Gear pumps of this type are used in various areas of technology to pump fluids, especially liquids, for example in vending machines or other systems in the food industry.
  • a gear pump usually has a delivery unit with two gears.
  • the fluid to be delivered is conveyed via the teeth of the mutually meshing gears, which generate a pressure gradient along the conveying direction.
  • a drive unit connected to the delivery unit which is often designed as an electric motor, is used to drive the gears.
  • One gear is usually driven directly by the drive unit and the other indirectly due to the mutually meshing teeth.
  • the delivery unit and the drive unit are often connected to one another via connecting elements that can be operated without tools, which enables such gear pumps to be quickly assembled and disassembled or individual components such as the drive unit to be replaced.
  • a gear pump for conveying a processing aid is known.
  • the drive and conveyor units are detachably connected via separate connecting elements, which are designed as multi-part clamping rings.
  • These are first aligned axially with each other so that two flange-like clamping areas on the one hand of the drive unit and on the other hand of the conveyor unit lie flat against each other.
  • the clamping rings are then manually placed around the flange-like clamping areas and tightened via an actuating element designed like a clamping screw with a wing nut.
  • the actuating element is connected to the clamping ring in an articulated manner at one end and is folded into a position tangential to the clamping area for clamping so that the wing nut engages behind a fork-shaped holding element.
  • the diameter of the clamping ring is reduced, whereby a clamping force is applied in the radial direction to the clamping area.
  • the clamping rings have inclined surfaces so that the radial clamping force is converted into an axial connecting force in the area of the flange-like clamping areas and is used to connect the drive and conveyor units.
  • the object of the invention is to provide a gear pump, a pump arrangement and a method, which are characterized in that the delivery and drive unit of the corresponding gear pumps can be connected to one another in a simple and error-free manner.
  • connecting elements are arranged on the conveyor unit and connecting elements on the drive unit and are designed to correspond to one another.
  • Such an arrangement enables a particularly simple and user-friendly connection or locking of the drive unit to the conveyor unit.
  • the same number of connecting elements is formed on the conveyor unit and the drive unit.
  • the connecting elements on the conveyor unit and on the drive unit are designed to correspond with respect to their respective geometry.
  • the connecting elements are designed to correspond with respect to their respective position on the conveyor unit and the drive unit, which can result in a particularly simple possibility of connecting the drive unit to the conveyor unit.
  • the connecting elements can be arranged directly on the conveyor unit and/or the drive unit.
  • the connecting elements can also be arranged indirectly via an intermediate element on the conveyor unit and/or the drive unit.
  • the intermediate element can optionally also have an adapter function, for example for arranging different drive units on one and the same conveyor unit.
  • the connecting elements are formed on mutually facing sides of the conveyor unit and the drive unit.
  • it can also be useful for connecting elements to be arranged on several sides of the conveyor and/or drive unit. This increases the flexibility with regard to the connection of conveyor unit and drive unit with different orientations to each other.
  • An advantageous embodiment provides that connecting elements are formed on flat fastening areas of the conveyor unit and/or the drive unit. After the locking elements have locked in place, a flat contact and thus a reliable connection is achieved.
  • the connecting elements are arranged at equal distances, in particular angular distances, relative to one another. Such an arrangement allows the conveyor unit and the drive unit to be easily connected to one another and is also advantageous with regard to a uniform transmission of forces between the conveyor unit and the drive unit. This makes it possible to achieve a particularly high-quality and firm connection between the conveyor unit and the drive unit.
  • the connecting elements are arranged at equal distances in the circumferential direction relative to one another, whereby a particularly uniform connection force can be generated.
  • the connecting elements are formed in one piece with the conveyor unit and/or the drive unit.
  • Such an arrangement is particularly advantageous with regard to a simple connection, since the connecting elements are designed to be captive.
  • such an embodiment is advantageous with regard to the production of the conveyor unit and/or the drive unit, for example by means of injection molding, since the connecting elements can be formed directly during the production of the conveyor unit and/or the drive unit.
  • the conveyor unit and the drive unit can be connected to one another in several assembly positions.
  • Such a design enables a simple, user-friendly connection of the conveyor unit to the drive unit, since the conveyor unit and the drive unit can be connected to one another in not just one, but in several assembly positions or orientations. It has also proven advantageous if the assembly positions differ with regard to the rotational orientation of the conveyor unit relative to the drive unit.
  • a further advantageous embodiment provides that the number of possible mounting positions corresponds to the number of corresponding connecting elements.
  • An increased number of mounting positions can offer advantages with regard to the arrangement of the conveyor and drive unit. In particular, in certain installation situations, accessibility to certain areas of the conveyor unit and/or the drive unit can be improved.
  • two possible mounting positions can be provided for two pairs of connecting elements.
  • three possible mounting positions can be provided for three pairs of connecting elements, etc. It is particularly preferred if four mounting positions are provided and selectable for four pairs of connecting elements.
  • Such an embodiment enables a quick and user-friendly connection of the drive unit to the conveyor unit, since the number of connecting element pairs can already be used to determine how many possible mounting positions there are.
  • the connecting elements form a bayonet connection.
  • a bayonet connection is particularly advantageous with regard to a simple and error-free locking connection of the drive unit with the conveyor unit.
  • a bayonet connection can provide a enable intuitive, repeatable, non-destructively detachable locking connection of the drive unit with the conveyor unit. Establishing a connection via a bayonet connection can be carried out easily and without risk of error, even by inexperienced assembly personnel.
  • the connecting elements are designed as bayonet hooks and/or corresponding recesses.
  • Such a design enables a bayonet connection to be easily produced.
  • the bayonet hooks are designed to engage in the corresponding recesses.
  • the geometric designs of the bayonet hooks and/or the recesses are adapted to one another or are designed to correspond.
  • the bayonet hooks have a substantially rectangular shape with a base and a locking part that spreads out at right angles from the base.
  • Such an arrangement allows a simple and easy-to-assemble connection using the bayonet connection.
  • the locking part that spreads out at right angles from the base can be used in a simple manner to create a high-quality, positive locking connection.
  • transverse spreading of the locking part from the base can also be provided in an angle range of 80° to 100° to the base.
  • the locking part points radially outwards or radially inwards.
  • the recesses have a plug-in area for inserting the bayonet hooks and a securing area for locking the bayonet hooks.
  • the locking area is designed to interact with the locking part of the bayonet hook.
  • the recesses are designed as circular ring segments, with the plug-in areas extending over one half of the circular ring segments and the securing areas being arranged in the other half of the circular ring segments. It is preferred if the geometry of the plug-in areas is designed to correspond to the geometry of the bayonet hooks, and in particular the locking part of the bayonet hooks. Furthermore, such an arrangement can be advantageous with regard to user-friendly assembly of the conveyor unit and drive unit.
  • the production of a bayonet connection can be made possible in an advantageous manner by sequentially inserting the bayonet hooks into the plug-in area of the recesses and then rotating the bayonet hooks relative to the recesses.
  • the securing areas extend flat and web-like from the outer radius of the circular ring segments in the radial direction over at least one third of the extent of the circular ring segments.
  • extensions of the securing areas of 10% to 50% and in particular 25% to 45% of the radial extent of the circular ring segments can also be provided.
  • the securing areas have a compensation ramp for tolerance compensation, which is designed to interact with the locking parts of the respective bayonet hooks.
  • the compensation ramp is preferably designed in such a way that it can deform reversibly when tolerances overlap.
  • the compensation ramp is arranged as an inclined plane on the securing area that rises in the circumferential direction of the circular ring segment and extends in particular over at least two thirds of the length of the securing area.
  • Such a design of the compensation ramp enables simple and user-friendly tolerance compensation.
  • the inclined plane can have a constant angle of rise or one that varies over the length of the compensation ramp.
  • the individual securing areas can have compensation ramps of the same design.
  • the drive unit and the conveyor unit are designed to be rotatable relative to one another about a rotation axis in order to fix or release the bayonet connection.
  • the drive unit and the conveyor unit can initially be inserted into one another in the axial direction along the rotation axis in the area of the connecting elements. and in a second step they are rotated relative to each other around an axis of rotation. This allows a snap-in connection between the drive unit and the conveyor unit that can be made quickly and safely, even by inexperienced operating personnel. Furthermore, such a connection can be easily released without causing any damage by reversing the process steps used to make the connection.
  • the rotation axis corresponds to the drive axis of the drive unit.
  • This enables an axisymmetric structure, whereby the drive unit and/or the conveyor unit can be rotated about the drive axis for connection.
  • the connection can be made by turning in one direction and the connection can be released by turning in the opposite direction.
  • the conveyor unit has at least two bayonet hooks and the drive unit has at least two corresponding recesses for the engagement of the bayonet hooks.
  • the conveyor unit has at least two bayonet hooks and the drive unit has at least two corresponding recesses for the engagement of the bayonet hooks.
  • the conveyor unit has at least three, four or five bayonet hooks for connection to at least three, four or five corresponding recesses arranged on the drive unit.
  • the bayonet hooks and the corresponding Recesses are arranged in a circle and evenly over the circumference.
  • the conveyor unit has at least three, four or five recesses and the drive unit has at least three, four or five bayonet hooks for engaging in the recesses.
  • a larger number of corresponding bayonet hooks and recesses has proven to be advantageous with regard to the mechanical load-bearing capacity of the connection.
  • the bayonet connection has a reverse rotation lock.
  • a reverse rotation lock can secure the delivery unit and the drive unit against undesirable loosening of the connection as a result of shocks and/or vibrations that can occur when the gear pump is in operation.
  • the reverse rotation lock can also act as a connection indicator to show that the drive unit and the delivery unit are correctly connected.
  • the anti-reverse locking device has at least one spring-loaded locking hook that interacts with at least one corresponding locking recess in a form-fitting manner.
  • Such a design enables the connection to be secured against reverse rotation in a simple and secure manner.
  • the locking hook is spring-loaded in the radial direction.
  • the locking recess can advantageously be adapted to the structural design of the locking hook in terms of its position and geometric shape.
  • the safety hook has a safety lug for engaging in a corresponding safety recess
  • a locking lug enables simple and effective anti-reverse locking.
  • the geometry of the locking lug is adapted to the geometry of the corresponding locking recess.
  • the at least one safety hook is arranged on the conveyor unit and the at least one safety recess is arranged on the drive unit.
  • the conveyor unit and the drive unit can be secured in a simple and safe manner against unwanted reversal and thus against unwanted loosening of the connection.
  • the drive unit it is also conceivable for the drive unit to have a safety hook which is designed to cooperate with at least one safety recess arranged on the conveyor unit to prevent reversal.
  • the anti-reverse locking device has a locking hook and several locking recesses into which the locking hook can engage depending on an assembly position.
  • Such an arrangement enables the conveyor unit and the drive unit to be connected in several assembly positions, whereby these can be secured against unintentional reversal.
  • the drive unit has at least two, preferably four and particularly preferably as many locking recesses around the circumference as there are connecting elements arranged on the drive unit or on the conveyor unit.
  • the conveyor unit can have several locking recesses distributed around the circumference of the fastening area.
  • connection elements form a snap hook connection.
  • a design like a bayonet connection, enables a simple and user-friendly locking connection of the drive unit to the conveyor unit.
  • the connecting elements are designed as spring-loaded locking tongues and/or corresponding recesses.
  • the locking tongues can be designed in such a way that they can be inserted into the corresponding recesses in a form-fitting manner.
  • the locking tongues have a locking area which is designed to interact in a form-fitting manner with a corresponding locking area of the recesses.
  • Such a construction allows a simple and error-free locking connection between the conveyor unit and the drive unit.
  • the locking connection can be created by simply inserting the locking tongues into the corresponding recesses.
  • the locking tongues have an insertion bevel for easy insertion into the recesses.
  • the insertion bevel can be designed as an inclined plane extending from the tip of the locking tongues in their axial direction.
  • the edge of the recesses can be designed to interact with the insertion bevel and support the springing of the locking tongues.
  • the locking tongues are designed in such a way that when inserted, they compress the recesses transversely to their insertion direction and when the connection position is reached, they rebound, whereby the locking areas lock together.
  • Such a design is advantageous with regard to easy connection of the drive unit to the conveyor unit by insertion in the axial direction.
  • the locking areas locked together can also serve as an indicator of a successful connection of the conveyor unit to the drive unit.
  • the locking tongues can have color-contrasting markings, in particular at their tip, as a connection indicator, which are visible when correctly locked and indicate a successful connection. Assembly errors can be avoided in this way.
  • the locking tongues are designed in such a way that they spring in transversely to the plug-in direction when a release force is applied that is opposite to the plug-in direction.
  • a release force is applied that is opposite to the plug-in direction.
  • the connection By applying the release force, the locking can be easily released.
  • the release force to be applied for release is selected in such a way that it cannot easily occur when the gear pump is in operation, which can prevent the snap hook connection from being released accidentally during operation.
  • the conveyor unit has at least two locking tongues and the drive unit has at least two corresponding recesses for the engagement of the locking tongues. This has proven to be advantageous with regard to a secure, symmetrical and resilient connection between the conveyor unit and the drive unit.
  • the drive unit has at least two locking tongues and the conveyor unit has at least two corresponding recesses for the engagement of the locking tongues.
  • the conveyor unit has three, four or five locking tongues for connection to three, four or five corresponding recesses arranged on the drive unit.
  • Such an arrangement is particularly advantageous for the mechanical load-bearing capacity of the connection between the conveyor unit and the drive unit. It is particularly advantageous if the three, four or five locking tongues or the three, four or five corresponding recesses are arranged in a circle at an equal distance from one another in the respective fastening area. It is also entirely conceivable for the drive unit to have three, four or five locking tongues for connection to three, four or five corresponding recesses arranged on the conveyor unit.
  • guide elements are proposed for guiding the plug-in movements when connecting and/or releasing the snap hook connection.
  • Such guide elements can simplify the production of the locking connection between the conveyor element and the drive element.
  • guide elements can serve as protection against incorrect assembly. It is particularly advantageous if the guide elements are designed as projections or recesses and have corresponding shapes.
  • the connecting elements are formed on at least one intermediate element, the intermediate element being attached to the conveyor unit and/or the drive unit.
  • the connecting elements are indirectly connected to the drive unit and/or the conveyor unit via the intermediate element.
  • the intermediate element can be designed in the manner of an adapter be adapted to the requirements of the connection between the conveyor unit and the drive unit.
  • different drive units and conveyor units can therefore also be connected to one another. This can be advantageous, for example, when replacing a less powerful drive unit with a more powerful one.
  • the intermediate element can be designed in the manner of a disc.
  • connecting elements are arranged in one piece on the conveyor unit and corresponding connecting elements are formed on an intermediate element which is arranged on the drive unit.
  • the intermediate element is detachably attached to the conveyor unit and/or the drive unit.
  • detachable attachment by means of fastening means such as screws or bolts can be preferred.
  • fastening means such as screws or bolts
  • Such an arrangement can enable the intermediate element to be changed quickly and easily.
  • the intermediate element can be replaced in a simple manner.
  • the intermediate element can also be permanently attached to the conveyor unit and/or the drive unit if this should prove to be advantageous for the respective application.
  • the intermediate element has a shaft bearing for supporting the intermediate shaft.
  • the shaft bearing is preferably positioned centrally and Type of a cylindrical collar on a substantially disc-shaped intermediate element.
  • the shaft bearing has a shaft seal ring for sealing the intermediate shaft.
  • a shaft seal ring enables the intermediate shaft to be easily sealed. Furthermore, such an arrangement makes it easy to specify the position of the shaft seal ring.
  • the intermediate shaft has an actuating contour which can be positively connected to a corresponding actuating contour arranged on at least one of the gears.
  • This gear is a driven gear.
  • At least one of the gears has a bearing contour for freely rotatable arrangement on a bearing axis.
  • Such a bearing contour has proven to be advantageous for mounting the gear on the bearing axis.
  • This gear is a co-rotating gear.
  • the actuating contours can be connected to one another in a form-fitting manner.
  • the actuating contour of the intermediate shaft is designed to correspond to the actuating contour of at least one of the gears and can be connected to it in a form-fitting manner.
  • Such a design enables a simple form-fitting connection of the intermediate shaft to at least one of the gears.
  • the driven gear of the gear pump has an actuating contour.
  • the actuating contour of the intermediate shaft is not designed to be insertable into the bearing contour.
  • Such a design means that the intermediate shaft cannot be connected to the non-driven gear, which has the bearing contour. This also helps to avoid assembly errors, since the intermediate shaft can only be connected to the driven gear intended for it.
  • actuating contours are designed in the form of a polygon, in particular a pentagon.
  • a polygon can be produced in a simple manner.
  • a polygon can be designed as the outer contour of a bolt or as the inner contour of a bore.
  • the bearing contour is designed as a round bore.
  • Such a round bore enables the non-driven gear to be easily mounted freely on the bearing axis.
  • the diameter of the round hole and the diameter of the polygon of the actuating contour are selected so that they cannot be inserted into one another. This enables the gear pump to be assembled easily and without risk of errors. Assembly errors due to incorrect connection of the intermediate shaft and/or the bearing axis to the gears can be prevented.
  • the conveyor unit has a plain bearing for supporting the intermediate shaft of the drive unit.
  • the plain bearing is arranged near the driven gear. This type of structural arrangement can reduce friction and wear, as angular errors between the intermediate shaft and the gear can be compensated for by the plain bearing.
  • the gears are arranged in a gear space delimited by a wall of the conveyor unit and the plain bearing is arranged in the wall.
  • the plain bearing is located in the immediate vicinity of the gears. Angular errors are effectively compensated.
  • the gear pump has a connection indicator that shows the connection between the delivery unit and the drive unit. If correctly locked, this connection indicator can be arranged so that it is visible to the assembly personnel and can show a successful connection. Assembly errors can thus be avoided.
  • connection indicator is formed on the anti-reverse device of the bayonet connection.
  • a pump arrangement with a gear pump and at least one valve unit according to claim 10 is proposed to solve the above-mentioned problem.
  • the same advantages previously mentioned in relation to the gear pump arise.
  • Such a pump arrangement advantageously enables control of the fluid flow.
  • the delivery unit of the gear pump be connected to a valve unit via tool-free connecting elements
  • Such a design enables a quick and user-friendly connection between the conveyor unit and the valve unit.
  • the connecting elements are designed as locking elements. This results in the same advantages as previously explained with regard to the connection between the conveyor unit and the drive unit.
  • the connecting elements form a bayonet connection as defined in claim 1.
  • the bayonet connection is designed in accordance with the previously described bayonet connection.
  • the connecting elements can also form a snap hook connection.
  • the snap hook connection is designed in accordance with the previously described snap hook connection.
  • gear pump is designed according to one or more of the features described above.
  • the representations in the Fig. 1 and Fig. 2 show a gear pump 1 with a delivery unit 2 for conveying a fluid and a drive unit 3 designed as an electric motor.
  • the drive unit 3 serves to operate the delivery unit 2, through which the fluid to be conveyed, which can be drinking water, for example, can flow via two connections 26 serving as inlet and outlet.
  • the drive unit 3 is detachably connected to the conveyor unit 2.
  • the connecting elements 7, 8 are provided.
  • the connecting elements 7, 8 are designed as locking elements and therefore allow a simple and error-free locking connection of the conveyor unit 2 and the drive unit 3.
  • the locking elements 7, 8 face each other and interact in a locking manner like a bayonet connection 50, cf. Fig. 2 Details of the bayonet connection 50 are explained below using the illustrations in the Fig. 9a to 14 will be explained in more detail.
  • the connecting elements 7 are arranged on one end of the conveyor unit 2 and interact with the connecting elements 8 arranged on the drive unit 3 in a locking manner. While the connecting elements 7 are arranged directly on the conveyor unit 2, the connecting elements 8 are arranged indirectly on the drive unit 3 via a disc-shaped intermediate element 6.
  • the indirect arrangement of the connecting elements 8 on the drive unit 3 has the advantage that the intermediate element 6 can be used as an adapter for connecting different drive units 3, for example with different operating principles, different performance, etc., to one and the same conveyor unit 2, depending on the application.
  • the drive-side connecting elements 8 it would also be conceivable for the drive-side connecting elements 8 to be arranged directly on the drive 3. It would also be conceivable for the connecting elements 7 to be formed on an intermediate element (not shown in the figures) connected to the conveyor unit 2.
  • FIG. 1 shows a separated state
  • the representation in Fig. 2 the assembled gear pump 1, in which the drive unit 3 and the delivery unit 2 are detachably connected to one another by mutual locking via the bayonet connection 50.
  • the end faces of the delivery unit 2 and the intermediate element 6 of the drive unit 3 lie flush and flat against one another and form a connection area 5.
  • the drive unit 3 of the gear pump 1 has a substantially cylindrical geometry and is designed as an electric motor.
  • the drive unit 3 has electrical connections 3.1. By supplying current to the drive unit 3, a drive shaft 3.2 is set in rotation, which is used to drive the delivery unit 3.
  • the drive unit 3 is a standard electric motor that is commercially available in a wide variety of designs, such as brushless or brushed electric motors of various power classes.
  • an intermediate shaft 14 extending between the drive 3 and the conveyor unit 2 is provided.
  • the intermediate shaft 14 is designed as a separate component in the embodiment.
  • the intermediate shaft 14 is connected to a drive shaft 3.2 of the drive unit 3, which is designed as a short axle stub, and on the other side to the conveyor unit 3.
  • the intermediate shaft 14 it would also be conceivable for the intermediate shaft 14 to be connected in one piece to the drive shaft 3.2. In this case, however, a standard motor could not be used.
  • the intermediate shaft 14 has a shaft connection 14.2 for connection to the drive unit 3.
  • the shaft connection 14.2 is cylindrical and sleeve-like and is an integral part of the intermediate shaft 14.
  • the shaft connection 14.2 is pressed onto the drive shaft 3.2 for connection to the drive unit 3.
  • the intermediate shaft 14 can in particular be made of a stainless steel with a minimum chromium content of 16%, which is approved for use in the food sector or for driving gear pumps 1 for pumping drinking water.
  • the drive shaft 3.2 of the drive unit 3 does not come into contact with the fluid to be pumped because the intermediate shaft 14 is pressed on like a shaft extension.
  • the drive unit 3 On one end face, the drive unit 3 has a disk-shaped intermediate element 6, which is detachably attached to the drive unit 3 via fastening means 23 designed as screws and corresponding holes 24.
  • the intermediate element 6 is essentially round.
  • the intermediate element 6 has the drive-side connecting elements 8, which are recesses 8.
  • the intermediate element 6 has a shaft bearing 13 for supporting the intermediate shaft 14.
  • the shaft bearing 13 is designed in the manner of a cylindrical collar and extends in the middle of the intermediate element 6 essentially perpendicular to its surface.
  • the conveyor unit 2 is essentially cuboid-shaped and has a housing 2.1 and a cover 2.2, which are connected to one another by means of cylindrical, dumbbell-shaped plug-in connection elements 22.
  • the plug-in connection elements 22 are inserted into correspondingly designed recesses 33 for connection and overlap the flat contact area between the housing 2.1 and the cover 2.2 on its lower and upper sides, see also Fig.4 and 9a .
  • the cover 2.2 has two tubular connections 26 serving as inlet and outlet, via which the conveyor unit 2 can be connected to other components of the respective hydraulic system (not shown).
  • the conveyor unit 2 On the side opposite the connections 26, the conveyor unit 2 has a flat fastening area B, on which the connecting elements 7 are formed in one piece.
  • the connecting elements 7 are as shown in Fig.1 designed as a bayonet hook.
  • the bayonet hooks 7 are arranged directly on the fastening area B.
  • they are arranged indirectly, via an intermediate element 6 on the fastening area B.
  • An inverse arrangement would also be conceivable, i.e. the bayonet hooks 7 are arranged on the drive side and the recesses 8 on the conveyor side.
  • the housing 2.1 and the cover 2.2 of the conveying unit 2 as well as the intermediate element 6 and all elements arranged thereon are preferably made of plastic by means of suitable processes, in particular injection molding processes. All components in contact with the fluid to be conveyed are suitable for use in the food or drinking water sector.
  • a gear chamber 35 is arranged inside the housing 2.1.
  • the gear chamber 35 is sealed from the cover 2.2 by means of a seal 25 designed as an O-ring.
  • Two gears 4.1 and 4.2 are arranged to rotate in the gear chamber 35.
  • the teeth of the driven gear 4.1 engage in the corresponding gaps of a second, co-rotating gear 4.2.
  • the co-rotating gear 4.2 is rotatably mounted parallel to the axis of the driven gear 4.1 on an axis 21 arranged in the housing 2.2.
  • the fluid to be conveyed flows around both gears 4.1, 4.2.
  • the co-rotating gear 4.2 is rotated in the opposite direction.
  • the connections 26 are connected to the inlet 31 and the outlet 32, which can be guided through the cover 2.2 or arranged on the side walls of the housing 2.1.
  • the driven gear 4.1 is plug-connected to the intermediate shaft 14 to drive the conveyor unit 2.
  • the transmission of the drive force from the intermediate shaft 14 to the driven gear 4.1 takes place via corresponding actuating contours 14.1 and 16.1.
  • the actuating contour 14.1 is designed as a pentagon, which is arranged as an outer contour at the end of the intermediate shaft 14 opposite the drive unit 3, cf. Fig. 6c .
  • the driven gear 4.1 has a corresponding pentagonal contour designed as an inner contour as the actuating contour 16.1, cf. Fig. 6b .
  • the actuating contour 14.1 is inserted into the actuating contour 16.1 to drive the driven gear 14.1.
  • the pentagonal design enables effective transmission of the torque.
  • the rotating gear 4.2 does not have an actuating contour, but rather a bearing contour 16.2 designed as a round bore, cf. Fig. 6a .
  • the geometries of the actuating contour 14.1 and the bearing contour 16.2 are selected such that the actuating contour 14.1 of the intermediate shaft 14 cannot be inserted into the bearing contour 16.2 of the rotating gear 4.2, cf. Fig.7 . This ensures that the intermediate shaft 14 can only be connected to the driven gear 4.1.
  • the bearing contour 16.2 is designed in such a way that the rotating gear 4.2 can only be connected to the corresponding axis 21 provided for it, see also Fig. 8b .
  • a shaft sealing ring 15 is provided, see. Fig.4 .
  • the shaft seal 15 is designed as a radial shaft seal.
  • the intermediate shaft 14 has a corresponding coating in the area of the shaft seal 15, or has been hardened to the corresponding hardness specification by means of Kolsterizing.
  • the edges of the actuating contour 14.1 designed as a pentagon are rounded.
  • Fig. 8b shows an enlargement of section VIII b according to Fig. 8a .
  • the driven gear 4.1 is, as previously explained, placed on the actuating contour 14.1 of the intermediate shaft 14.
  • a plain bearing 17 is located in the housing 2.1 of the conveyor unit 2.
  • the arrangement of the plain bearing 17 in the wall 2.3 of the conveyor unit 2 near the gear 4.1 enables additional guidance of the intermediate shaft 14.
  • the plain bearing 17 can be designed as a recess in the wall 2.3, provided the wall is made of a suitable material.
  • the plain bearing 17 can be inserted into the wall 2.3 as a separate component and designed, for example, as a plain bearing bush.
  • the axis 21 of the rotating gear 4.2 is also mounted in the area of this gear 4.2 by means of a plain bearing.
  • the plain bearing of the rotating gear 4.2 can also be integrally mounted on the gear 4.2 or inserted into it as a separate plain bearing.
  • FIG. 9a shows the fastening area B arranged on one side of the conveyor unit 2.
  • Four bayonet hooks 7 are arranged at a certain radial distance from the center of the fastening area B.
  • the bayonet hooks 7 are arranged at regular intervals point-symmetrically to a central round hole in the fastening area B, so that there is an angle of 90° between the bayonet hooks 7.
  • the bayonet hooks 7 are formed in one piece with the housing 2.1. Based on the illustration in Fig. 14 It can be seen that the bayonet hooks 7 are essentially L-shaped with a rectangular base and have a base 7.1 and a locking part 7.2.
  • the Base 7.1 extends vertically from the surface of the fastening area B.
  • the locking part 7.2 extends transversely to the base 7.1.
  • the lower edge of the locking part 7.2 extends parallel to the surface of the fastening area B.
  • the outer edges of the bayonet hook 7 are bevelled or have chamfers, which can facilitate insertion into corresponding recesses 8.
  • the intermediate element 6 attached to the drive unit 3 in the present embodiment is designed as a flat round disk, cf. Fig. 9b
  • the intermediate element 6 has four continuous recesses 8, which are designed in the manner of circular ring segments 34.
  • the recesses 8 are designed in such a way that they can interact with the bayonet hooks 7 to connect the conveyor unit 2 to the drive unit 3.
  • the recesses 8 are arranged point-symmetrically on a common circular path around a central round hole. The angular distance between the recesses is therefore 90°.
  • the recesses 8 each have a plug-in area 8.1, cf. Fig.10 .
  • This plug-in area 8.1 is adapted to the geometry of the locking part 7.2 of the bayonet hook 7 and enables the bayonet hook 7 to be inserted.
  • the plug-in area 8.1 extends in the circumferential direction over approximately half the circumferential length of the recess 8.
  • a securing area 8.2 is arranged in the other circumferential half of the recess 8. This securing area 8.2 is designed to interact with the locking part 7.2 of the bayonet hook 7. It extends flat and like a web from the outer radius of the recess 8 to approximately one third of its radial length, cf. Fig.10 .
  • the securing area 8.2 is arranged in the lower area of the recess 8, its thickness corresponds approximately to half the thickness of the intermediate element 6, cf. Fig. 12a .
  • the recesses 8 have bevels for easy connection to the bayonet hooks 7.
  • the conveyor unit 2 and the drive unit 3 are designed to be rotatable relative to each other, with the rotation axis D corresponding to the drive axis A, see also Fig.3 .
  • the securing area 8.2 of the recess 8 and the locking part 7.2 of the bayonet hook 7 come into mutual engagement, cf. Fig. 12a .
  • No additional tools are required to produce the bayonet connection 50.
  • the four bayonet hooks 7 engage behind the securing areas 8.2 of the recesses 8, whereby they are positively locked.
  • the bayonet connection 50 has a reverse rotation lock 10 to prevent it from being turned back.
  • the reverse rotation lock 10 serves to prevent unwanted release due to vibrations or shocks during operation of the gear pump 1.
  • the delivery unit 2 has a safety hook 10.1, see. Fig. 9a .
  • the safety hook 10.1 is arranged radially on the outside of the fastening area B and is designed as a spring arm that is hinged on one side and springs in the radial direction.
  • the safety hook 10.1 also has a protruding safety nose 10.2, which extends at the free end of the safety hook 10.1 essentially perpendicular to the surface of the fastening area B.
  • the safety nose 10.2 engages in a correspondingly designed recess 10.3 in the intermediate element 6, see. Fig. 9d and 9e .
  • the safety hook 10.1 can be manually disengaged from the recess 10.3.
  • a release force sufficient to release the bayonet connection 50 can be generated by mutual rotation of the conveyor unit 2 relative to the drive unit 3.
  • the anti-reverse device 10 has a dual function. It not only serves to prevent accidental loosening, but also shows, as a connection indicator 36 that can be read from the outside, that the bayonet connection 50 between the conveyor unit 2 and the drive unit 3 is correctly locked. This is because the locking lug 10.2 visible from the outside and the recess 10.3 only engage with one another when the bayonet connection 50 is correctly locked.
  • the intermediate element 6 has a total of four recesses 10.3, which are arranged at equal distances over the circumference of the intermediate element 6, cf. e.g. Fig. 9e .
  • the one locking lug 10.2 can engage in any of these recesses 10.3.
  • the drive unit 3 can thus be connected to the conveyor unit 2 in any of four orientations or assembly positions, which differ in the rotational position of the drive unit 3 about its drive axis A.
  • the securing areas 8.2 each have a compensation ramp 9 for tolerance compensation.
  • the compensation ramp 9 is designed in such a way that it can interact with the locking part 7.2 of the corresponding bayonet hook 7.
  • the compensation ramp 9 is arranged over approximately two thirds of the length of the securing area 8.2 in the circumferential direction and essentially covers its entire width in the radial direction.
  • the compensation ramp 9 is designed as an inclined plane rising in the circumferential direction and extends in the assembled state in the direction of the locking part 7.2 of the bayonet hook 7, see also Fig. 12b . Together with the locking part 7.2 of the bayonet hook 7, the compensation ramp 9 can be used to compensate for tolerances and ensure a play-free connection between the conveyor unit 2 and the drive unit 3.
  • the compensation ramp 9 is designed in such a way that it can deform reversibly if there is a tolerance overlap.
  • FIG. 15 to 20 show a second embodiment, which does not fall within the scope of the claims and which, in contrast to the first embodiment, does not have a bayonet connection 50 but rather a snap hook connection 60, but otherwise corresponds to the first embodiment in all relevant features.
  • the snap hook connection 60 differs from the previously described bayonet connection 50 essentially in the structural design of the connecting elements 11, 12.
  • the representation in Fig. 15 shows a fastening area B arranged on one side of the conveyor unit 2.
  • Four recesses 12 are arranged at a certain radial distance from the center of the fastening area B.
  • the recesses 12 are arranged at equal distances and tangentially to a central round hole in the fastening area B, so that there is an angle of 90° between the recesses 12.
  • the recesses 12 are designed as essentially rectangular openings in the fastening area B, see. Fig. 19 .
  • the recesses 12 each have a locking area 12.1, which is arranged in the manner of an edge on the back of the fastening area B, see also Fig. 20 .
  • Between the recesses 12, further, also rectangular openings are arranged on the fastening area B.
  • the fastening area B has four guide elements 20, which are arranged as rectangular recesses designed in the manner of notches on the edge of the central round hole. The guide elements 20 are aligned with the recesses 12.
  • the locking tongues 11 of the snap hook connection 60 are again formed on an intermediate element 6, cf. Fig. 18 .
  • the locking tongues 11 have a tab-like basic shape and extend essentially transversely to the surface of the intermediate element 6 into the same direction as the shaft bearing 13, which is designed as a cylindrical collar.
  • the locking tongues 11 are designed to be resilient in the radial direction in the manner of a spring-loaded cantilever arm.
  • the four locking tongues 11 are arranged at an equal distance from one another on the same radius so that they are aligned with the recesses 12 of the conveyor unit 2 to create a locking connection, cf. Fig. 16 .
  • the locking tongues 11 In the area of their tip, the locking tongues 11 have a locking area 11.1, which is designed in the manner of an edge transverse to the tab-like base body of the locking tongue 11.
  • the tip of the locking tongues 11 is provided with an insertion bevel 11.2, by means of which the insertion of the locking tongues 11 into the corresponding recesses 12 of the conveyor unit 2 can be made easier.
  • the intermediate element 6 also has four guide elements 19, which are designed as rectangular, nose-like projections on the cylindrical collar of the shaft bearing 13. The guide elements 19 are aligned with the locking tongues 11.
  • the drive unit 3 is moved in the insertion direction R along the drive axis A towards the conveyor unit 2 and inserted into the recesses 12, see. Fig. 15 and 16 .
  • the tips of the locking tongues 11 in the area of the fastening area B hit the edges of the corresponding recesses 12.
  • This causes the spring-loaded locking tongues 11 to spring in a radial direction.
  • the insertion bevels 11.2 facilitate plugging in.
  • the connection position is reached according to Fig. 17 the locking tongues 11 spring out transversely to the piercing direction R, whereby the locking areas 11.1 of the locking tongues 11 engage with the locking areas 12.1 of the recesses 12, see also Fig. 20 .
  • the correspondingly designed guide elements 19, 20 of the intermediate element 6 and the fastening area B also engage with one another.
  • the tip of the locking tongue 11 can have a suitable colored marking, which is visible from the outside in the locked connection position and is designed as a connection indicator 36.
  • a marking can be arranged in an area between the insertion bevel 11.2 and the locking area 11.1. This makes it easy to recognize whether the snap hook connection 60 has been made correctly. If the locking tongues 11 are not completely locked into the recesses 12, an edge of the recess 12 covers the colored marking, which allows the assembly personnel to recognize an assembly error.
  • the pump arrangements 100 each have a delivery unit 2, a drive unit 3 connected thereto and one or more valve units 18.
  • the conveyor unit 2 has at least two connecting elements 27, 28 for detachably connecting the conveyor unit 2 to a valve unit 18.
  • the connecting elements 27, 28 can be arranged directly on the conveyor unit 2 or indirectly via an adapter-like intermediate element 37.
  • the connecting elements 27, 28 are designed as bayonet hooks and corresponding recesses. and arranged laterally on the conveyor unit 2, so that the valve unit 18 can be connected to the drive unit 3 by means of a bayonet connection 70 in a direction transverse to the drive unit 3.
  • the housing of the drive unit 3 and the valve housings of the valve units 18 can move in the same direction (cf. Fig. 21 ) or in the opposite direction (cf. Fig. 22 ), or perpendicular to each other (cf. Fig. 23 ).
  • the connecting elements for connecting the conveyor unit 2 to the valve unit 18 can also be designed as locking tongues and corresponding recesses for producing a snap hook connection.
  • the bayonet connection 70 and the snap hook connection can be designed according to the previously described locking connections between the conveyor unit 2 and the drive unit 3.
  • valve units 18 can also be connected to each other by means of corresponding connecting elements 29, 30, cf. Fig. 23 . In this way, series arrangements of valves can be produced for carrying out various switching operations.
  • the valve units 18 can be connected to one another via intermediate elements 37.
  • the connecting elements 29, 30 of the valve units 18 are designed as locking elements and can be designed in particular as bayonet hooks and corresponding recesses or as locking tongues and corresponding recesses.
  • the connecting elements 27, 28, 29, 30 are designed corresponding to the connecting elements 7, 8, 11, 12 of the conveyor unit 2 or the drive unit 3.
  • the drive unit 3 is moved axially aligned in the plug-in direction R along the drive axis A towards the conveyor unit 2, whereby the intermediate shaft 14 engages in a corresponding round hole in the fastening area B. Furthermore, the bayonet hooks 7 engage in the plug-in areas 8.1 of the respective recesses 8, cf. Fig. 9c . As soon as the intermediate element 6 and the conveyor unit 2 are in contact with one another, the drive unit 3 and thus the intermediate element 6 are rotated clockwise relative to the conveyor unit 2. The locking parts 7.2 of the bayonet hooks 7 engage with the securing areas 8.2 of the respective recesses.
  • the securing nose 10.2 of a reverse rotation lock 10 engages in a corresponding securing recess 10.3 of the intermediate element 6, see. Fig. 9e .
  • tolerance compensation is carried out when the conveyor unit 2 and the drive unit 3 rotate relative to one another by the compensation ramps 9, which can deform to compensate for tolerances, cf. Fig. 12b .
  • the drive unit 3 is moved in the plug-in direction R along the drive axis A towards the conveyor unit 2, whereby the intermediate shaft 14 engages in a corresponding round hole in the fastening area B. Furthermore, the locking tongues 12 engage with their tips in the recesses 11, see. Fig. 17 .
  • the insertion bevels 11.2 of the locking tongues 11 come into contact with the edges of the recesses 12, whereby the locking tongues 11 spring radially inwards with further axial displacement.
  • the connection position is reached, the locking tongues 11 spring out automatically and the locking area 11.2 of the locking tongues 11 locks into the locking area 12.1 of the respective recess 12, see. Fig. 20 .
  • the gear pump 1 described above, the pump arrangement 100 and the method for connecting the delivery unit 2 and the drive unit 3 of a gear pump 1 are characterized by a simple and error-free connection of the drive unit 3 with the conveyor unit 2, which can also be carried out safely by inexperienced assembly personnel.

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

Claims (11)

  1. Pompe à engrenages pour le refoulement d'un fluide avec une unité de refoulement (2) présentant au moins deux roues dentées (4.1, 4.2) et une unité d'entraînement (3) entraînant les roues dentées (4.1, 4.2), qui sont reliés entre elles de manière amovible par l'intermédiaire d'éléments de liaison (7, 8) actionnables sans outil,
    caractérisée en ce que
    les éléments de liaison (7, 8) sont réalisés sous forme d'éléments d'encliquetage et forment une liaison à baïonnette (50) qui présente une sécurité anti-retour (10), la sécurité anti-retour (10) présentant au moins un crochet de sécurité (10.1) réalisé sous forme élastique, qui coopère par complémentarité de forme avec au moins un évidement de sécurité (10.3) correspondant.
  2. Pompe à engrenages selon la revendication 1, caractérisée en ce que des éléments de liaison (7) sont agencés sur l'unité de refoulement (2) et des éléments de liaison (8) sont agencés sur l'unité d'entraînement (3) et sont réalisés de manière à se correspondre.
  3. Pompe à engrenages selon la revendication 1, caractérisée en ce que les éléments de liaison (7, 8) sont réalisés sous forme de crochets à baïonnette et/ou d'évidements correspondants.
  4. Pompe à engrenages selon la revendication 3, caractérisée en ce que les crochets à baïonnette (7) présentent une forme essentiellement rectangulaire avec un socle (7.1) et une partie d'encliquetage (7.2) qui s'écarte du socle à angle droit.
  5. Pompe à engrenages selon la revendication 3 ou 4, caractérisée en ce que les évidements (8) présentent une zone d'emboîtement (8.1) pour l'insertion des crochets à baïonnette (7) et une zone de sécurité (8.2) pour l'encliquetage des crochets à baïonnette (7).
  6. Pompe à engrenages selon la revendication 5, caractérisée en ce que les zones de sécurité (8.2) présentent une rampe d'égalisation (9) pour l'égalisation des tolérances, qui sont conçues pour coopérer avec les parties d'encliquetage (7.2) des crochets à baïonnette (7) respectifs.
  7. Pompe à engrenages selon l'une quelconque des revendications précédentes, caractérisée en ce que les éléments de liaison (7, 8) sont réalisés sur au moins un élément intermédiaire (6), l'élément intermédiaire (6) étant fixé à l'unité de refoulement (2) et/ou à l'unité d'entraînement (3).
  8. Pompe à engrenages selon l'une quelconque des revendications précédentes, caractérisée en ce que l'unité d'entraînement (3) est reliée fonctionnellement aux roues dentées (4.1, 4.2) par l'intermédiaire d'un arbre intermédiaire (14) pour l'entraînement des roues dentées (4.1, 4.2).
  9. Pompe à engrenages selon l'une quelconque des revendications précédentes, caractérisée par un indicateur de liaison (36) indiquant la liaison entre l'unité de refoulement (2) et l'unité d'entraînement (3).
  10. Agencement de pompe avec une pompe à engrenages (1) et au moins une unité de soupape (18),
    caractérisé en ce que
    la pompe à engrenages (1) est réalisée selon l'une quelconque des revendications précédentes.
  11. Procédé pour relier de manière amovible une unité de refoulement (2) et une unité d'entraînement (3) d'une pompe à engrenages (1) par l'intermédiaire d'éléments de liaison (7, 8) actionnables sans outil, caractérisé en ce que
    les éléments de liaison (7, 8) sont encliquetés les uns avec les autres, et forment une liaison à baïonnette (50) qui présente une sécurité anti-retour (10), qui présente au moins un crochet de sécurité (10.1) réalisé sous forme élastique, qui coopère par complémentarité de forme avec au moins un évidement de sécurité (10.3) correspondant.
EP21204258.4A 2021-10-22 2021-10-22 Pompe à engrenage Active EP4170127B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DK21204258.4T DK4170127T3 (da) 2021-10-22 2021-10-22 Tandhjulspumpe
EP21204258.4A EP4170127B1 (fr) 2021-10-22 2021-10-22 Pompe à engrenage
ES21204258T ES2994854T3 (en) 2021-10-22 2021-10-22 Gear wheel pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP21204258.4A EP4170127B1 (fr) 2021-10-22 2021-10-22 Pompe à engrenage

Publications (2)

Publication Number Publication Date
EP4170127A1 EP4170127A1 (fr) 2023-04-26
EP4170127B1 true EP4170127B1 (fr) 2024-08-28

Family

ID=78414230

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21204258.4A Active EP4170127B1 (fr) 2021-10-22 2021-10-22 Pompe à engrenage

Country Status (3)

Country Link
EP (1) EP4170127B1 (fr)
DK (1) DK4170127T3 (fr)
ES (1) ES2994854T3 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102023103046A1 (de) * 2023-02-08 2024-08-08 A. u. K. Müller GmbH & Co KG. Pumpsystem mit mehreren fluidtechnischen Modulen
DE102023123609A1 (de) * 2023-09-01 2025-03-06 A. u. K. Müller GmbH & Co KG. Fluidmodul

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2325173C (fr) * 1999-11-03 2004-05-11 Wildfire Fire Equipment Inc. Element de raccordement pour pompe
US6325604B1 (en) * 2000-03-29 2001-12-04 Benjamin R. Du Plastic gear pump housing
US20060083631A1 (en) * 2004-10-13 2006-04-20 Walbro Engine Management, L.L.C. Fuel pump assembly
EP3282086B1 (fr) 2016-08-10 2024-07-31 Groeneveld-BEKA GmbH Pompe, en particulier pompe a roue dentee destinee au transport d'auxiliaires technologiques
FR3060669B1 (fr) * 2016-12-20 2020-11-27 Coutier Moulage Gen Ind Pompe a engrenage a plaques et pions de centrage hydrauliques.

Also Published As

Publication number Publication date
EP4170127A1 (fr) 2023-04-26
DK4170127T3 (da) 2024-11-11
ES2994854T3 (en) 2025-02-03

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