EP4202181B1 - Pompe à engrenage - Google Patents

Pompe à engrenage Download PDF

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Publication number
EP4202181B1
EP4202181B1 EP21216262.2A EP21216262A EP4202181B1 EP 4202181 B1 EP4202181 B1 EP 4202181B1 EP 21216262 A EP21216262 A EP 21216262A EP 4202181 B1 EP4202181 B1 EP 4202181B1
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EP
European Patent Office
Prior art keywords
gear
chamber
flow
space
flushing
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
EP21216262.2A
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German (de)
English (en)
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EP4202181A1 (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 DK21216262.2T priority Critical patent/DK4202181T3/da
Priority to EP21216262.2A priority patent/EP4202181B1/fr
Publication of EP4202181A1 publication Critical patent/EP4202181A1/fr
Application granted granted Critical
Publication of EP4202181B1 publication Critical patent/EP4202181B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F01C21/02—Arrangements of bearings
    • 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
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/005—Removing contaminants, deposits or scale from the pump; Cleaning
    • 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
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • 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
    • F04C2/086—Carter

Definitions

  • the invention relates to a gear pump for conveying a fluid flow, the direction of flow of which can be reversed by switching between a conveying and a flushing mode, with two gears arranged in a gear space and an auxiliary space that is flow-connected to the gear space, the fluid flow being dependent on a main flow component flowing through the gear space and a secondary flow portion flowing at least partially through the adjacent space.
  • a further subject of the invention is a method for conveying a fluid flow with such a gear pump.
  • Gear pumps of this type are used in various areas of technology to convey fluid flows, for example as a feed pump for oil or other lubricants or liquids, in beverage machines or other systems in the beverage industry, etc.
  • a gear pump usually has a gear space that accommodates the gears and has an inlet and an outlet for the fluid flow.
  • One of the gears is usually driven to rotate via a shaft and the other is designed to rotate.
  • the drive for the shaft is arranged outside the gear space and the shaft is guided into the gear space via a feedthrough.
  • shaft sealing rings are used, which enable a separation between the fluid-flowing, gear-side end of the shaft and the dry, drive-side end of the shaft.
  • these shaft seals cannot be attached directly in or on the gear space. Rather, it is necessary to arrange the shaft sealing ring in an adjacent space, which is usually fluidly connected to the gear space via the passage having a certain annular gap and is sufficiently dimensioned to accommodate the shaft seal.
  • a pressure gradient is created in the gear space via the teeth of the mutually meshing rotating gears, which causes a fluid flow from the inlet to the outlet of the gear space.
  • a rinsing operation is also provided in order to clean the gear pump and other fluid-carrying components at regular intervals clean.
  • this flushing operation the direction of the fluid flow is changed, ie it no longer flows from the inlet to the outlet of the gear space, but in the opposite direction from its outlet to the inlet.
  • a cleaning agent is often added to the fluid flow during rinsing operation.
  • the rinsing fluid that has been stored in the adjacent room during rinsing mode and has been mixed with cleaning agents only returns through the outflow opening into the gear room after switching to conveying mode again and mixes with the fluid to be conveyed, for example the milk from a fully automatic coffee machine.
  • the means for increasing the proportion of secondary flow in the flushing operation results in different flow proportions in the conveying and flushing mode, which means that an improved flushing of the adjacent space can be achieved in the flushing mode without impairing the delivery performance in the conveying mode.
  • a build-up of flushing fluid in the adjacent room can occur due to the improved flushing can be avoided.
  • an advantageous embodiment provides that the gears are connected to a drive unit via an intermediate shaft.
  • the intermediate shaft can be detachably or permanently connected to a drive shaft of the drive unit.
  • the intermediate shaft is made of a material that is adapted to the fluid to be conveyed. This can, for example, prevent corrosion on the intermediate shaft.
  • the choice of material for the intermediate shaft can be adapted to the hygiene requirements of the fluid or the area of application, which are particularly increased in the food sector.
  • one gear can be driven via the intermediate shaft and the other gear is designed to rotate.
  • components of the drive unit are arranged in a drive space, the gear space being arranged in an area through which fluid flows and the drive space being arranged in a dry area, with a seal for fluid-tight separation of the gear space in front of the drive space being arranged in the adjacent space.
  • Another advantage is that the drive unit can be replaced in a simple and user-friendly manner, since it has no direct connection to the area through which fluid flows.
  • the seal is also there Easy to access due to its arrangement in the adjacent room and can be easily replaced in a way that is easy to install and maintain.
  • the intermediate shaft extends from the gear space through the adjacent space into the drive space.
  • the continuous extension of the intermediate shaft enables low-loss power transmission between the drive unit and the driven gear.
  • sealing the intermediate shaft in the adjacent space leads to a separation of the fluid-flowing area and the dry area of the gear pump, which simplifies sealing.
  • the intermediate shaft is sealed in the adjacent space via a shaft guide ring.
  • a shaft seal as a standard part to seal the shaft is not only advantageous from a cost perspective, but also with regard to error-prone and easy installation of the shaft seal. It is particularly preferred if the shaft sealing ring is designed in the manner of a radial shaft sealing ring.
  • a plain bearing for supporting the intermediate shaft is arranged between the gear space and the adjacent space.
  • a plain bearing enables the compensation of angular errors between the driven gear and the intermediate shaft in the immediate vicinity of the gear, which can achieve a reduction in friction and wear.
  • the plain bearing can be a hydrodynamic plain bearing.
  • the plain bearing can be arranged in the area where the intermediate shaft passes through.
  • a further embodiment provides that the secondary flow portion flows at least partially through an annular gap formed in the area of the plain bearing. In the area of the plain bearing or the bushing there is a small annular gap and thus a small proportion of bypass flow.
  • the gear pump has an outflow opening that flows between the gear space and the adjacent space.
  • an outflow opening designed in the manner of a ventilation, enables fluid to flow out of the adjacent space into the gear space in a simple and reliable manner.
  • the outflow opening can enable the adjacent space to be completely emptied.
  • the outflow opening allows fluid to drip from the adjacent space into the gear space when the gear pump is at a standstill.
  • the gear pump can be arranged accordingly during operation so that the fluid can drip under the influence of gravity. In this way, long-term accumulations of fluid in the adjacent room can be avoided, since the adjacent room is emptied after each pumping process.
  • the outflow opening can also be used to continuously flush the adjacent room during conveying operation. From a design and manufacturing perspective, it is particularly advantageous to design the outflow opening as a through hole between the gear space and the adjacent space.
  • the cross-sectional area of the annular gap is smaller than the cross-sectional area of the outflow opening.
  • Such a configuration ensures that the adjacent space can be thoroughly rinsed during conveying operation, since, due to the larger cross-sectional area, a larger amount of fluid can always flow out of the adjacent space through the outflow opening than flows in through the smaller annular gap. Furthermore, this configuration allows the gear pump to be at a standstill a complete dripping of fluid from the adjacent space into the gear space.
  • the secondary flow portion flows in conveying operation along a secondary flow path which leads through the annular gap, the secondary space and the outflow opening.
  • a secondary flow path which leads through the annular gap, the secondary space and the outflow opening.
  • the means have a closable flushing channel which extends between the gear space and the adjacent space.
  • the closable flushing channel is preferably designed as a through hole between the gear space and the adjacent space with a locking means that interacts with the through hole.
  • the flushing channel can be designed transversely to the gear space and essentially straight.
  • the rinsing channel can run essentially parallel to the axis of rotation of the gears, which allows easy demoulding during primary production of the gear space.
  • the closable design makes it possible to keep the flushing channel closed during conveying operation and to open it during flushing operation.
  • pressure losses can be kept low due to the low proportion of bypass flow when the flushing channel is closed.
  • Such pressure losses do not play a role in flushing mode and can occur due to the higher A good flushing effect can be achieved with the side flow component when the flushing channel is open.
  • the flushing channel is arranged in an area of the gear space in which there is an overpressure during conveying operation and / or if the outflow opening is arranged in an area of the gear space in which there is a negative pressure during delivery operation .
  • both a sufficient flow and flushing of the adjoining room in the conveying operation as well as an increase in the bypass flow proportion in the flushing operation of the adjoining room can be achieved.
  • the dripping of fluid from the adjacent space can be ensured when the gear pump is at a standstill.
  • the arrangement of the outflow opening in an area of the gear space in which there is a negative pressure during delivery operation supports the fluid flowing out of the adjacent space into the gear space.
  • the flushing channel and/or the outflow opening is arranged below one of the gears, in particular below the driven gear.
  • Such an arrangement of the flushing channel and/or outflow opening has proven to be useful in terms of production technology and also enables a particularly good flow through the flushing channel and/or the outflow opening.
  • the flushing channel and/or the outflow opening are arranged outside the area through which the main flow component flows, so that disturbances to the main flow component are avoided.
  • the means have a closing device for closing the flushing channel, which is designed and arranged in such a way that flow through the flushing channel is only possible in flushing mode.
  • a locking device allows targeted adjustment an increased proportion of bypass flow in flushing operation.
  • a locking device allows simple and user-friendly control or adjustment of the fluid flow within the gear pump.
  • the closing device can be used to block undesired flow paths in conveying operation, but desired flow paths in flushing operation, in a simple and reliable manner.
  • the closing device is designed as a check valve. This enables a particularly simple and error-prone design. A reliable and easily controllable closing and opening of the flushing channel can be achieved for a variety of operating states.
  • the locking device is arranged at the gear-side end of the flushing channel. This is advantageous from a flow perspective, as larger accumulation areas in the flushing channel are avoided.
  • such an arrangement enables particularly simple and error-prone assembly of the locking device, for example via the gear space.
  • an arrangement of the locking device at the gear-side end of the flushing channel is particularly easy to maintain, as it enables the locking device to be easily replaced, for example in the event of a defect.
  • the closing device has a movably mounted closing element, which is designed and arranged in such a way that the closing device automatically opens or closes the flushing channel when switching between the conveying and flushing modes.
  • a movably mounted closing element which is designed and arranged in such a way that the closing device automatically opens or closes the flushing channel when switching between the conveying and flushing modes.
  • the closing element can in particular be a movable one Be designed as a ball or similar component, or alternatively as an articulated element, for example in the form of a flap or hatch.
  • Force support for the closing element is also conceivable, for example in the form of a spring preload or another restoring element to support the opening or closing movements.
  • a preferred embodiment provides that the closing element rests in an open position of the closing device on one of the gears, in particular on an end face of one of the gears, and/or in a closed position on a closing surface of the flushing channel.
  • This allows defined positions for the closing element to be specified in the open position and the closed position of the closing device. If the closing element rests against one of the gears in the open position of the closing device in the manner of a stop, this involves little manufacturing effort since no separate stop is required.
  • the closing surface of the flushing channel can be designed as a sealing surface.
  • the closing device has a guide for guiding the opening and closing movements of the closing element.
  • a guide increases the reliability of the locking device, since failures due to jamming or tilting of the locking element can be avoided by the guide.
  • the flushing operation can be used in particular to flush the gears, the gear space and other fluid-carrying components of the gear pump.
  • the reversal of the fluid flow between the conveying operation and the flushing operation can be particularly advantageous Way can be generated by reversing the direction of rotation of the gears.
  • the drive unit can be switched from a forward run for the conveying operation to a reverse run for the rinsing operation.
  • the main flow portion is larger than the secondary flow portion. This enables efficient operation of the gear pump with low power losses and the pumpable fluid volume can be maximized. In addition, such a ratio between the main flow portion and the secondary flow portion can reduce the risk of leaks and leaks as well as other damage in the area of the secondary flow.
  • the gear space has at least one compensation space for compensating for the crush volume of the gears.
  • the compensation space can advantageously serve to equalize pressure in the toothing area of the gears.
  • such a compensation space can reduce pressure peaks that arise in the fluid in the area of the mutually meshing gears. A reduction in pressure peaks leads to a reduction in the mechanical stress on the components of the gear pump and in particular on the gears.
  • the loads acting on the gear bearings can be reduced.
  • the compensation space is designed as a channel-like recess in a wall of the gear space.
  • the dimensions of the compensation space can be adapted to the crushing volume of the gears.
  • the compensation space is designed as a channel-like, rectangular recess is designed in the manner of a pinch groove.
  • Such a pinch groove can be manufactured in a particularly simple and quick manner. Arranging the compensation space on the wall of the gear space, on which the outflow opening and the flushing channel are also arranged, has proven to be particularly advantageous. On the one hand, this enables simple production and, on the other hand, favorable flow conditions within the gear space.
  • the compensation space is arranged in an area of the gear space in which the teeth of the gears are in mutual engagement. This enables a direct flow connection between the squeezing volume of the gears and the compensation space. In this way, a reliable pressure equalization between the squeeze volume and the compensation space can be achieved.
  • the gear-side end of the flushing channel is fluidly connected to the compensation space, in particular opening into it via the closing device.
  • a flow connection can be formed between the gear-side end of the flushing channel and the compensation space.
  • This is advantageous in terms of efficient fluid flow.
  • such a structural design has proven to be advantageous in terms of production technology.
  • the flushing channel and/or the closing device has at least one mouth opening for flow connection to the compensation space.
  • the mouth opening can have a larger flow cross section than the flushing channel.
  • Such a mouth opening advantageously enables a directed flow of the fluid, in particular this makes it possible to specifically introduce or discharge the fluid into or out of the flushing channel. Also enables a mouth opening a flow connection between the gear space and the rinsing channel and/or the closing device, even in the event that a tooth of the gear covers the gear-side end of the smaller rinsing channel or the closing device when at a standstill.
  • the flow cross section of the flushing channel is at least the same size as the flow cross section of the outflow opening.
  • the flow cross section of the flushing channel is larger than the flow cross section of the outflow opening.
  • the secondary flow portion flows in the rinsing operation along a secondary flow path, which leads via the outflow opening into the adjacent space and from the open rinsing channel and the annular gap into the gear space.
  • a secondary flow path enables thorough flushing of the secondary space in the flushing mode by means of a higher secondary flow proportion of the total fluid flow. This is particularly useful for applications in the food industry, such as in beverage vending machines, in order to achieve hygienic cleanliness of the area of the gear pump through which fluid flows.
  • the gear pump With regard to a construction of the gear pump that is as easy to assemble as possible, it has proven to be advantageous if it has a delivery unit having the gear wheels and a drive unit driving the gear wheels, which are releasably connected to one another via connecting elements that can be operated without tools, the connecting elements are designed as locking elements.
  • Such a configuration enables a particularly simple and easy-to-assemble connection of the conveyor unit and the drive unit. Due to the design of the connecting elements as locking elements, a simple and error-prone connection of the drive unit to the conveyor unit results.
  • the locking elements allow precise and repeatable assembly with constant connecting force, even after multiple loosening, in a user-friendly manner, which can be carried out safely even by inexperienced assembly personnel. Assembly errors, which could result, for example, from incorrect positioning of the connecting elements or insufficient connecting force, are avoided.
  • 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 regard to their respective geometry.
  • the connecting elements are designed to correspond with respect to their respective positions 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 be optional also an adapter function, for example for arranging different drive units, on one and the same conveyor unit.
  • connecting elements are designed on sides of the conveyor unit and the drive unit that face one another.
  • it can also make sense for connecting elements to be arranged on several sides of the conveyor and/or drive unit. This increases flexibility with regard to the connection of the conveyor unit and drive unit with different orientations to one another.
  • An advantageous embodiment provides that connecting elements are formed on flat fastening areas of the conveyor unit and/or the drive unit. After locking the locking elements, there is a flat contact and thus a reliable connection.
  • the connecting elements are arranged at uniform 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 in terms of a uniform transmission of forces between the conveyor unit and the drive unit. This makes it possible to achieve a particularly high-quality and strong 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 connecting force can be generated.
  • the connecting elements are formed in one piece with the conveyor unit and/or the drive unit.
  • One like this 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 processes, 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 configuration 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 not only in one, but in several assembly positions or orientations. It has also proven to be advantageous if the assembly positions differ with regard to the rotational alignment of the conveyor unit relative to the drive unit.
  • a further advantageous embodiment provides that the number of possible assembly positions corresponds to the number of corresponding connecting elements.
  • An increased number of assembly 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 assembly positions can be provided for two pairs of connecting elements.
  • three possible assembly positions can be provided for three pairs of connecting elements, etc. It is particularly preferred if four assembly positions are provided and selectable for four pairs of connecting elements.
  • Such a design enables a quick and user-friendly connection of the drive unit to the conveyor unit, since the number of connecting element pairs can be used to determine how many possible assembly positions there are.
  • the connecting elements form a bayonet connection.
  • a bayonet connection is particularly advantageous with regard to a simple and error-prone locking connection of the drive unit to the conveyor unit.
  • a bayonet connection can enable a locking connection of the drive unit to the conveyor unit that is intuitive, repeatable and non-destructively releasable for the assembly personnel. Establishing a connection via a bayonet connection can be easy and error-free even for inexperienced assembly personnel.
  • the connecting elements are designed as bayonet hooks and/or corresponding recesses.
  • Such a design enables a bayonet connection to be made easily. It is particularly advantageous if the bayonet hooks are designed to engage in the corresponding recesses. In this context, it can be advantageous if the geometric configurations 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.
  • the locking part which spreads out at right angles from the base, can be used in a simple manner to create a high-quality, positive locking connection.
  • you can also Transverse spreads of the locking part from the base can be provided in an angular 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 securing area is designed to interact with the latching part of the bayonet hook for latching.
  • 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 of 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 insertion area of the recesses and then rotating the bayonet hooks relative to the recesses.
  • the locking part of the bayonet hook can be locked in a form-fitting manner with the securing area of the recesses.
  • extensions can also be used be provided over a proportion between 30% and 70% and in particular 40% and 60% of the width of the circular ring segments.
  • other geometric relationships in particular wider or less wide plug-in areas, are also conceivable, adapted to the requirements of the connection between the conveyor and drive unit.
  • the securing areas extend flat and web-like from the outer radius of the circular ring segments in the radial direction over at least a 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 in the event of a tolerance overlap.
  • the compensation ramp is arranged on the securing area as an inclined plane rising in the circumferential direction of the circular ring segment, which in particular extends 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.
  • tolerances of different sizes can be compensated for.
  • the Inclined plane can have a constant rise angle or one that varies over the length of the compensation ramp.
  • the individual security areas can have equalization ramps of the same design.
  • the drive unit and the conveyor unit are designed to be rotatable relative to one another about an axis of rotation for fixing or releasing the bayonet connection.
  • the drive unit and the conveyor unit can first be inserted into one another in the axial direction along the axis of rotation in the area of the connecting elements and, in a second step, can be rotated relative to one another about an axis of rotation.
  • This allows a snap-in connection between the drive unit and the conveyor unit that is simple and can be established quickly and safely even by inexperienced operating personnel.
  • such a connection can be released in a simple, non-destructive manner by reversing the process steps carried out for the connection.
  • the axis of rotation corresponds to the drive axle of the drive unit.
  • the drive unit and/or the conveyor unit can be rotated around the drive axis for connection.
  • the connection can be made by rotating in one direction of rotation and the connection can be released by rotating in the opposite direction of rotation.
  • the conveyor unit has at least two bayonet hooks and the drive unit has at least two corresponding recesses for engaging the bayonet hooks.
  • the conveyor unit has at least two bayonet hooks and the drive unit has at least two corresponding recesses for engaging 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 circularly 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 strength of the connection.
  • the bayonet connection has an anti-rotation lock.
  • an anti-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 during operation of the gear pump.
  • the anti-reverse lock can also serve as a connection indicator to indicate a correct connection of the drive unit and the conveyor unit.
  • the anti-rotation lock has at least one resilient locking hook, which interacts in a form-fitting manner with at least one corresponding locking recess.
  • Such a design makes possible a simple and secure anti-twist lock for the connection.
  • the securing hook is designed to be resilient in the radial direction.
  • the securing recess can advantageously be adapted to the structural design of the securing hook in terms of its position and geometric shape.
  • the securing hook has a securing lug for engaging in a corresponding securing recess.
  • a safety lug enables simple and effective anti-reverse protection.
  • the geometry of the securing lug is adapted to the geometry of the corresponding securing recess.
  • the at least one securing hook is arranged on the conveyor unit and the at least one securing 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 turning back and thus against unwanted loosening of the connection.
  • the drive unit has a safety hook, which is designed to cooperate with at least one safety recess arranged on the conveyor unit to prevent rotation.
  • the anti-reverse lock has a locking hook and a plurality of locking recesses into which the locking hook can engage depending on a mounting 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 turning back.
  • the drive unit has at least two, preferably four and particularly preferably as many securing recesses over the circumference as connecting elements are arranged on the drive unit or on the conveyor unit.
  • the conveyor unit can have a plurality of securing recesses distributed over the circumference of the fastening area.
  • a further advantageous alternative embodiment provides that the connecting elements form a snap hook connection.
  • Such a configuration 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 resilient 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 positively with a corresponding locking area of the recesses.
  • Such a construction allows a simple and error-prone 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 cooperate with the insertion bevel and support the deflection of the locking tongues.
  • the locking tongues are designed in such a way that when they are inserted, they deflect the recesses transversely to their insertion direction and rebound when the connecting position is reached, whereby the locking areas lock together.
  • Such a construction is advantageous with regard to a simple connection of the drive unit to the conveyor unit by inserting it 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 colored markings, in particular at their tip, as a connection indicator, which are visibly arranged 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 deflect transversely to the plugging direction when a release force applied counter to the plugging direction is reached.
  • a release force applied counter to the plugging direction is reached.
  • the connection By applying the release force, the locking can be easily removed.
  • the releasing force to be applied for releasing is selected so that it cannot easily occur during operation of the gear pump, which means that unwanted loosening of the snap hook connection during operation can be prevented.
  • the conveyor unit has at least two locking tongues and the drive unit has at least two corresponding recesses for engaging the locking tongues. This has proven to be advantageous in terms of 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 engaging 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 strength of the connection between the conveyor unit and the drive unit.
  • the three, four or five locking tongues or the three, four or five corresponding recesses are arranged in a circle at a uniform distance from one another on the respective fastening area.
  • the drive unit can 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 plugging movements when connecting and/or releasing the snap hook connection.
  • Such guide elements can simplify the production of the locking connection between the conveying 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 shapes that correspond to one another.
  • 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 adapted in the manner of an adapter to the requirements of the connection between the conveyor unit and the drive unit.
  • different drive units and conveyor units can 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 disk. In this context, it has proven to be advantageous if 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.
  • a releasable attachment using fasteners such as screws or bolts may be preferred.
  • fasteners such as screws or bolts
  • Such an arrangement can enable a simple and quick change of the intermediate element.
  • 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 turns out to be advantageous for the respective application.
  • the intermediate element has a shaft bearing for supporting the intermediate shaft.
  • the shaft bearing is preferably in the middle and behind Type of cylindrical collar formed on a substantially disk-shaped intermediate element. Together with the plain bearing arranged in the area of the conveyor unit, a two-point bearing of the intermediate shaft can advantageously result.
  • the intermediate shaft has an actuation contour which can be positively connected to a corresponding actuation contour arranged on at least one of the gears.
  • This gear is the 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 storing the gear on the bearing axle.
  • This gear is the co-rotating gear.
  • the actuation contours can be connected to one another in a form-fitting manner.
  • the actuation contour of the intermediate shaft is designed to correspond to the actuation contour of at least one of the gears and can be connected to it in a form-fitting manner.
  • Such a configuration enables a simple, positive connection of the intermediate shaft to at least one of the gears.
  • the driven gear of the gear pump has an actuation contour.
  • the actuation contour of the intermediate shaft is not designed to be insertable into the bearing contour.
  • Such a configuration enables the intermediate shaft not to be connected to the non-driven gear, which has the bearing contour can. This also allows assembly errors to be avoided, as the intermediate shaft can only be connected to the driven gear wheel intended for this purpose.
  • actuation contours are designed in the manner of a polygon, in particular a pentagon. Such a design has proven to be advantageous with regard to low-loss power transmission.
  • 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 hole.
  • the bearing contour is designed as a round bore. Such a round hole enables the non-driven gear to be easily and freely rotatable on the bearing axis.
  • the diameter of the round bore and the diameter of the polygon of the actuation contour are selected so that they cannot be inserted into one another. This enables simple and error-prone assembly of the gear pump. Assembly errors due to incorrect connection of the intermediate shaft and/or the bearing axle 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 close to the driven gear. Such a structural arrangement can reduce friction and wear, since 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 limited by a wall of the conveyor unit and the plain bearing is arranged in the wall.
  • the plain bearing is in close proximity to the gears. Angular errors are effectively compensated for.
  • the gear pump has a connection indicator indicating the connection between the delivery unit and the drive unit. If correctly locked, this connection indicator can be visible to the assembly personnel and indicate a successful connection. Assembly errors can be avoided in this way.
  • connection indicator is formed on the anti-rotation lock of the bayonet connection and/or on the locking tongue of the snap hook connection.
  • a pump arrangement with a gear pump and at least one valve unit is proposed, the gear pump being designed according to one or more of the features described above.
  • the same advantages mentioned above with regard to the gear pump arise.
  • Such a pump arrangement advantageously enables the fluid flow to be controlled.
  • the delivery unit of the gear pump is connected to a valve unit via connecting elements that can be operated without tools.
  • Such a design enables a quick and user-friendly connection between the delivery unit and the valve unit.
  • the connecting elements are designed as locking elements. This results in the same advantages that were already explained previously with regard to the connection between the conveyor unit and the drive unit.
  • the connecting elements form a bayonet connection.
  • the bayonet connection is designed in accordance with the bayonet connection described above.
  • the connecting elements can also form a snap hook connection.
  • the snap hook connection is designed in accordance with the snap hook connection described above.
  • a method according to claim 13 is proposed to solve the above-mentioned problem.
  • the same advantages previously mentioned in relation to the gear pump arise.
  • such a method enables the adjacent space to be thoroughly rinsed in the rinsing mode.
  • the gear pump be 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 is used to operate the delivery unit 2, which has two connections 26 serving as inlet and outlet from the fluid to be conveyed, in which it For example, drinking water, milk, coffee, etc. can act, can flow through.
  • the gear pump 1 is characterized by good hygiene properties in both delivery and flushing mode and can be installed in a particularly easy-to-assemble manner.
  • 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 latching elements and therefore allow a simple and error-prone latching connection of the conveyor unit 2 and the drive unit 3.
  • the locking elements 7, 8 face each other and work together in a locking manner in the manner of a bayonet connection 50, cf. Fig. 2 . Details of the bayonet connection 50 are described below based on the illustrations in the 9a to 14 will be explained in more detail.
  • the connecting elements 7 are arranged on an end face of the conveyor unit 2 and act with the connecting elements arranged on the drive unit 3 8 snap together. 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 disk-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 power or the like, 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 unit 3. It would also be conceivable for the connecting elements 7 to be formed on an intermediate element that is not shown in the figures and is connected to the conveyor unit 2.
  • FIG. 1 shows a separated state
  • FIG. 2 the mounted gear pump 1, in which the drive unit 3 and the delivery unit 2 are releasably connected to one another via the bayonet connection 50 by mutual locking.
  • the end faces of the conveyor 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 is of essentially cylindrical geometry and designed as an electric motor.
  • the drive unit 3 has electrical connections 3.1.
  • a drive shaft 3.2 is set in rotation, which is used to drive the conveyor unit 3.
  • the drive unit 3 is a commercially available standard electric motor in a wide variety of designs, such as those available as brushless or brushed electric motors of various performance 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 exemplary embodiment.
  • the intermediate shaft 14 is connected to a drive shaft 3.2 of the drive unit 3 designed as a short stub axle 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.
  • 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 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 conveyed due to the intermediate shaft 14, which is pressed on in the manner of a shaft extension.
  • the drive unit 3 On one end face, the drive unit 3 has a disk-shaped intermediate element 6, which is releasably attached to the drive unit 3 via fastening means 23 designed as screws and corresponding corresponding bores 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 and has a housing 2.1 and a cover 2.2, which are connected to one another by means of cylindrical, dumbbell-shaped plug connection elements 22.
  • the plug 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 the bottom and top, cf. also Fig. 4 and 9a .
  • the cover 2.2 has two tubular connections 26 serving as inlet and outlet, via which the delivery 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.
  • the bayonet hooks 7 are arranged directly on the fastening area B. Alternatively, it is also conceivable that these are arranged indirectly, via an intermediate element 6, on the fastening area B. An inverse arrangement would also be conceivable, i.e. to arrange the bayonet hooks 7 on the drive side and the recesses 8 on the delivery side.
  • the housing 2.1 and the cover 2.2 of the conveyor unit 2 as well as the intermediate element 6 and all elements arranged thereon are preferably made of plastic using suitable processes, in particular injection molding processes. All components that come into contact with the fluid to be pumped are suitable for use in the food and drinking water sectors and in particular for use in beverage vending machines.
  • a gear space 35 is arranged inside the housing 2.1.
  • the gear space 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 rotatably arranged in the gear space 35.
  • the teeth of the driven gear 4.1 engage in the corresponding gaps of a second co-rotating gear 4.2.
  • the 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 driven gear 4.1 is plug-connected to the intermediate shaft 14 to drive the conveyor unit 2.
  • the transmission of the driving force from the intermediate shaft 14 to the driven gear 4.1 takes place via corresponding actuation contours 14.1 and 16.1.
  • the actuating contour 14.1 is designed as a pentagon, which is arranged as an outer contour on 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 actuation contour 16.1, cf. Fig. 6b .
  • the actuation contour 14.1 is inserted into the actuation contour 16.1 to drive the driven gear 14.1.
  • the pentagonal design enables effective transmission of torque.
  • the co-rotating gear 4.2 does not have an actuation contour, but rather a bearing contour 16.2 designed as a round bore, cf. Fig. 6a .
  • the geometries of the actuation contour 14.1 and the bearing contour 16.2 are selected so that the actuation contour 14.1 of the intermediate shaft 14 cannot be inserted into the bearing contour 16.2 of the co-rotating gear 4.2, cf. Fig. 7 . In this way it is ensured 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 intended for this purpose, see also Fig. 8b .
  • a shaft sealing ring 15 is provided, cf. Fig. 4 .
  • the shaft sealing ring 15 is designed as a radial shaft sealing ring.
  • the intermediate shaft 14 has a corresponding coating in the area of the shaft sealing ring 15 or has been hardened to the corresponding hardness specification by means of colsterization.
  • the edges of the pentagonal operating contour 14.1 are rounded.
  • Fig. 8b shows an enlargement of section VIII b according to Fig. 8a .
  • the driven gear 4.1 is, as explained above, plugged onto the actuating contour 14.1 of the intermediate shaft 14.
  • a plain bearing 17 is arranged in a passage 114 of the housing 2.1 of the conveyor unit 2 in the immediate vicinity of the gear 4.1.
  • 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 in the manner of a two-point bearing.
  • 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 possible effects of angular offsets for example due to angular tolerances of the drive unit 3, which become greater the greater the distance to the plain bearing 17, can thereby be reduced in the area of the gear 4.1.
  • This enables the gear pump 1 to run smoothly, which can also reduce wear on the gears 4.1 and 4.2.
  • the axis 21 of the co-rotating gear 4.2 is mounted in the area of this gear 4.2 by means of a plain bearing.
  • the plain bearing of the co-rotating gear 4.2 can also be inserted in one piece on the gear 4.2 or as a separate plain bearing in it.
  • 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 beveled or have chamfers, which can make insertion into corresponding recesses 8 easier.
  • the intermediate element 6 attached to the drive unit 3 in the present exemplary embodiment is, as explained, designed in the manner of 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 so 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 bore. 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 to be inserted 7.
  • 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 half of the circumference of the recess 8. This securing area 8.2 is designed to cooperate with the locking part 7.2 of the bayonet hook 7. It extends flat and web-like from the outer radius of the recess 8 to about a 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 chamfers for easy connection to the bayonet hooks 7.
  • the conveyor unit 2 and the drive unit 3 are designed to be rotatable relative to one another, with the axis of rotation D corresponding to the drive axis A, cf. 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 locked in a form-fitting manner.
  • the bayonet connection 50 has a reverse rotation lock 10 to protect against reverse rotation.
  • the anti-reverse lock 10 serves to protect against unwanted loosening caused by vibrations or shocks during operation of the gear pump 1.
  • the delivery unit 2 has a safety hook 10.1, cf. Fig. 9a .
  • the securing hook 10.1 is arranged radially on the outside of the fastening area B and is designed as a spring arm articulated on one side and resilient in the radial direction.
  • the securing hook 10.1 has a projecting securing lug 10.2 on, which extends at the free end of the securing hook 10.1 essentially perpendicular to the surface of the fastening area B.
  • the securing lug 10.2 engages in a correspondingly designed recess 10.3 in the intermediate element 6, cf. 9d and 9e .
  • the securing hook 10.1 can be manually disengaged from the recess 10.3.
  • a sufficient release force to release the bayonet connection 50 can be generated by mutually rotating the conveyor unit 2 relative to the drive unit 3.
  • the anti-reverse device 10 has a dual function. It not only serves to avoid unwanted loosening, but also shows, as a connection indicator 36 that can be read from the outside, a correctly locked bayonet connection 50 between the conveyor unit 2 and the drive unit 3. Because only when the bayonet connection 50 is correctly locked are the securing lug 10.2, which is visible from the outside, and the recess 10.3 in engagement with one another.
  • the intermediate element 6 has a total of four recesses 10.3, which are arranged at a uniform distance over the circumference of the intermediate element 6, cf., for example. Fig. 9e .
  • the one securing 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 four orientations or assembly positions, which differ in the rotational position of the drive unit 3 about its drive axis A.
  • the security areas 8.2 each have a compensation ramp 9 for tolerance compensation.
  • the compensation ramp 9 is designed so that it can interact with the locking part 7.2 of the corresponding bayonet hook 7.
  • the compensation ramp 9 is about two thirds of the length of the Securing area 8.2 is arranged on this 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, in the assembled state, extends in the direction of the locking part 7.2 of the bayonet hook 7, see also Fig. 12b .
  • the compensation ramp 9 can serve 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 in the event of a tolerance overlap.
  • FIG. 15 to 20 show a second embodiment, 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 regular intervals and tangentially to a central round bore of 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, cf. Fig. 19 .
  • the recesses 12 each have a locking area 12.1, which is arranged like an edge on the back of the fastening area B, see also Fig. 20 .
  • 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 bore. The guide elements 20 are aligned with the recesses 12.
  • the locking tongues 11 of the snap hook connection 60 are 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 in 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 resilient cantilever arm.
  • the four locking tongues 11 are arranged at a uniform distance from one another on the same radius, so that they are aligned with the recesses 12 of the conveyor unit 2 to establish 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 transversely 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 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, cf. 15 and 16 .
  • the tips of the locking tongues 11 abut the edges of the corresponding recesses 12 in the area of the fastening area B.
  • the resilient locking tongues 11 spring in the radial direction.
  • the insertion bevels 11.2 make insertion easier.
  • the connection position is reached Fig. 17 the locking tongues 11 spring out transversely to the piercing direction R, with the locking areas 11.1 of the locking tongues 11 locking with the locking areas 12.1 of the recesses 12, see also Fig. 20 .
  • the conveyor unit 2 and the drive unit 3 are thus locked together in the axial direction. Since the recesses 12 have essentially the same width as the tab-like locking tongues 11, relative rotation of the drive unit 3 relative to the conveyor unit 2 is also blocked. No additional tools are required to produce the snap hook connection 60.
  • 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 incompletely locked with the recesses 12, an edge of the recess 12 covers the colored marking, which means that the assembly personnel can recognize an assembly error.
  • the pump arrangements 100 each have a delivery unit 2, a drive unit 3 connected to it and one or more valve units 18.
  • the conveyor unit 2 has at least two connecting elements 27, 28 for releasably 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 are arranged laterally on the conveyor unit 2, so that the valve unit 18 can be connected to the drive unit 3 in a direction transverse to the drive unit 3 by means of a bayonet connection 70.
  • 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 ) extend.
  • the connecting elements for connecting the conveyor unit 2 to the valve unit 18 can also be designed as locking tongues and corresponding recesses to produce a snap hook connection.
  • the bayonet connection 70 and the snap hook connection can be designed in accordance with the previously described locking connections between the conveyor unit 2 and the drive unit 3.
  • the valve units 18 can also be connected to one another by means of corresponding connecting elements 29, 30, cf. Fig. 23 . This allows series arrangements of valves to be produced to carry out various switching operations. Alternatively, 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 latching elements and can in particular be designed as bayonet hooks and corresponding recesses or as latching tongues and corresponding recesses.
  • the connecting elements 27, 28, 29, 30 are preferably designed to correspond to the connecting elements 7, 8, 11, 12 of the conveyor unit 2 or the drive unit 3.
  • a method for tool-free, detachable connection of the conveyor unit 2 and the drive unit 3 is described below.
  • the drive unit 3 is moved axially aligned in the plug-in direction R along the drive axis A towards the conveyor unit 2, with the intermediate shaft 14 engaging in a corresponding round bore 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 lie flat against each other, 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 lock with the securing areas 8.2 of the respective recesses.
  • the securing lug 10.2 of a reverse rotation lock 10 snaps into a corresponding securing recess 10.3 of the intermediate element 6, cf. Fig. 9e .
  • tolerance compensation occurs when the conveyor unit 2 and the drive unit 3 are mutually rotated by the compensation ramps 9, which can deform to compensate for the tolerance, cf. Fig. 12b .
  • Such a bayonet connection 50 between conveyor unit 2 and drive unit 3 is released using the same steps described above in reverse order. Furthermore, the directions of rotation and insertion are reversed.
  • the drive unit 3 is moved towards the conveyor unit 2 in the plug-in direction R along the drive axis A, with the intermediate shaft 14 engaging in a corresponding round bore in the fastening area B. Furthermore, the locking tongues 12 engage with their tips in the recesses 11, cf. 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 deflect radially inwards during further axial displacement.
  • the locking tongues 11 spring out automatically and the locking area 11.2 of the locking tongues 11 locks with the locking area 12.1 of the respective recess 12, cf. Fig. 20 .
  • the gear pump 1 and the pump arrangement 100 are characterized by a simple and error-prone connection of the drive unit 3 to the delivery unit 2, which can also be carried out safely by inexperienced assembly personnel.
  • gear pump 1 and the pump arrangement 100 lies in improved hygiene properties in both the pumping and rinsing mode. This is explained in detail below.
  • FIG. 24a and b show further views of the gear pump 1 for conveying a fluid stream F, which show how the fluid stream F flows through the gear pump 1 in the conveying and rinsing mode.
  • a gear space 35 is arranged in the delivery unit 2, which has an inlet 31 and an outlet 32 for the fluid.
  • the inlet 31 and the outlet 32 can be fluidly connected outside the gear space 35 via connections 26 with various components of the fluid circuit or the delivery system and arranged in any way.
  • the connection 26 connected to the inlet 31 is guided, for example, through the cover 2.2 of the conveyor unit 2, cf. Fig. 26 .
  • the conveying operation represents the essential operating mode of the gear pump 1, in which, for example, drinking water, milk or coffee is conveyed in a drinks machine to provide or prepare drinks.
  • the fluid flows in the direction of flow S 1 promoted from the inlet 31 to the outlet 32, cf. Fig. 24a .
  • the fluid enters the gear space 35 through the inlet 31 and flows into several pocket-like spaces delimited by the teeth of the gears 4.1, 4.2 and the wall of the gear space 35.
  • the gears 4.1 and 4.2 By rotating the gears 4.1 and 4.2 in opposite directions, the fluid is conveyed mainly along the outer wall of the gear space 35 to the outlet 32. According to the arrow representation in Fig.
  • the driven gear 4.1 rotates clockwise in conveying mode and the co-rotating gear 4.2 rotates counterclockwise.
  • the rotation of the gears 4.1, 4.2 creates a pressure difference between the inlet 31 and the outlet 32 in the gear space 35.
  • the flow direction S 2 of the fluid is reversed, cf. Fig. 24b .
  • the fluid flows from the outlet 32 to the inlet 31.
  • the direction of rotation of the gears 4.1, 4.2 is reversed.
  • the driven gear 4.1 rotates in the rinsing mode as shown in Fig. 24b counterclockwise and the co-rotating gear 4.2 correspondingly clockwise.
  • the driven gear 4.1 is operatively connected to an intermediate shaft 14.
  • the intermediate shaft 14 extends from the drive unit 3 into the gear space 35 of the conveyor unit 2. This is a media separation the dry, drive-side area of the fluid-flowing, delivery or gear-side area of the gear pump 1 is required, which is explained below using the illustrations in Fig. 25 and 26 is explained.
  • the drive unit 3 is located in the dry area of the gear pump 1, through which fluid does not flow.
  • the drive unit 3 has the intermediate element 6, which is attached to the front side and has the shaft bearing 13 for supporting the intermediate shaft 14.
  • the intermediate element 6 is accommodated in a drive space 103 of the housing 2.1 of the conveyor unit 2.
  • the drive room 103 is located in the dry area of the conveyor unit 2.
  • an auxiliary space 101 adjoins the drive space 103 in the axial direction along the axis of rotation D.
  • the secondary space 101 is located between the drive space 103 and the gear space 35, viewed in the axial direction of the axis of rotation D.
  • the shaft seal ring 15 encloses the intermediate shaft 14 along its circumference in a fluid-tight manner. In this way, media separation takes place in the adjacent space 101 between the drive-side, dry area and the gear-side, fluid-flowing area of the gear pump 1. As shown in Fig. 25 The dry area is therefore located along the axis of rotation D to the left of the shaft sealing ring 15 and to the right of it is the area through which fluid flows.
  • the passage 114 with the already described plain bearing 17 for supporting the intermediate shaft 14 adjoins the adjacent space 101 along the axis of rotation D in the direction of the gear space 35.
  • the gear space 35 is arranged along the axis of rotation D behind the plain bearing 17, in which the intermediate shaft 14 with the actuation contour 14.1 engages in the actuation contour 16.1 of the driven gear 14.1.
  • a rotational movement of the Intermediate shaft 14 is transmitted to the driven gear 4.1 via the actuation contours 14.1, 16.1.
  • the adjacent space 101 and the gear space 35 are fluidly connected.
  • the fluid can flow from the gear space 35 through an annular gap 105 formed in the area of the feedthrough 114 into the adjacent space 101.
  • the annular gap 105 results from the design, since a certain amount of play is provided in the area of the bushing 114 or the plain bearing 17, which is designed as a hydrodynamic plain bearing, and the intermediate shaft 14.
  • the secondary space 101 is fluidly connected to the gear space 35 via the annular gap 105, fluid flows from the gear space 35 through the annular gap 105 into the secondary space 101 during operation of the gear pump 1. This fluid can accumulate and accumulate in the secondary space 101.
  • gear pump 1 has a further flow connection between the gear space 1 and the adjacent space 101, which will be explained below with reference to the illustration in Fig. 26 is explained.
  • the additional flow connection between the gear space 35 and the adjacent space 101 is designed as a bore-like outflow opening 104, as a ventilation, so to speak.
  • the outflow opening 104 extends from an area of the gear space 35 below the driven gear 4.1 essentially parallel to the axis of rotation D of the intermediate shaft 14 into the adjacent space 101.
  • the cross-sectional area of the outflow opening 104 is larger than the cross-sectional area of the annular gap 105. In this way ensures that a larger volume of fluid can flow through the outflow opening 104 than through the annular gap 105.
  • the outflow opening 104 is arranged in an area of the gear space 35 in which a negative pressure prevails during conveying operation.
  • the outflow opening 104 is formed near the inlet 31.
  • the arrangement in the negative pressure area of the gear space 35 makes it possible for fluid to flow from the adjacent space 101 into the gear space 35 and not to be conveyed or pressed in the opposite direction from the gear space 35 through the outflow opening 104 into the adjacent space 35. In this way, a flow from the adjacent space 101 through the outflow opening 104 into the gear space 35 can be achieved during conveying operation.
  • the outflow opening 104 is arranged and designed in such a way that when the gear pump 1 is at a standstill, ie when the gears 4.1, 4.2 are not rotating, it allows fluid to drip from the adjacent space 101 into the gear space 35 due to the influence of gravity. In this way, accumulations and congestion of fluid in the adjacent room 101 are avoided.
  • a flow path runs through the annular gap 105, the secondary space 101 and the outflow opening 104 in addition to the main flow.
  • This flow path corresponds to a secondary flow path, with the main flow path running in the flow direction S 1 in the gear space 35 from the inlet 31 to the outlet 32.
  • the portion of the fluid flow F that flows along the main flow path is hereinafter referred to as the main flow portion H and the portion of the fluid flow F that flows along the secondary flow path is referred to as the secondary flow portion N.
  • the secondary flow portion N flows partially through the gear space 35, in particular between the inlet 31 and the annular gap 105 and between the outflow opening 104 and the outlet 32.
  • the secondary flow portion N of the total fluid flow F is influenced by various parameters. It depends, for example, on the operating point of the gear pump 1, the pressures that can be achieved, the viscosity of the fluid and the dimensions of the outflow opening 104 and the annular gap 105. As a rule, however, the bypass flow portion N is less than 20%, in particular less than 5% and, in a preferred embodiment, less than 1% of the total fluid flow F. In conveying operation, a larger bypass flow portion N ensures better flushing of the adjacent space 101. A smaller bypass flow portion N On the other hand, it ensures efficient operation of the gear pump 1, which is why the bypass flow share N in delivery operation is generally kept as low as possible.
  • the gear pump 1 has means 102 for increasing the bypass flow portion N in the rinsing mode.
  • the basic idea behind the use of the means 102 is to set a low bypass flow proportion N in the delivery operation, which means that a good delivery rate and efficiency of the gear pump 1 can be achieved. In the flushing mode, however, the secondary flow proportion N should be increased by means 102 in order to achieve better flushing of the secondary space 101.
  • the means 102 are formed by a flushing channel 106 extending between the gear space 25 and the adjacent space 101.
  • This flushing channel 106 forms an additional flow connection between the gear space 35 and the adjacent space 101, which can only be flowed through in flushing mode, but not in conveying mode.
  • the flushing channel 106 is arranged below the driven gear 4.1 in an area of the gear space 35 in which there is usually an overpressure in the conveying operation and correspondingly a negative pressure in the flushing operation. Due to this negative pressure in the flushing mode, the fluid accumulated in the adjacent space 101 flows through the flushing channel 106 into the gear room 35.
  • the secondary flow path in the flushing mode therefore runs via the outflow opening 104 and possibly the annular gap 105 in the area of the feedthrough 114 into the adjacent space 101 and through the flushing channel 106 back into gear room 35. A gathering and accumulation of flushing fluid in the adjacent room 101 is avoided and the adjacent room 101 is thoroughly rinsed.
  • flushing fluid containing cleaning agent will flow back into the gear space 35 during conveying operation and contaminate the fluid. Since the flow cross section of the flushing channel 106 is larger than that of the outflow opening 104 and in the present exemplary embodiment even larger than the sum of the flow cross sections of the outflow opening 104 and the annular gap 105, more fluid can flow through the flushing channel 106 from the adjacent space 101 into the gear space 35 than in flows into the next room 101. In summary, the flushing channel 106 enables the bypass flow proportion N to be increased in the flushing operation.
  • the secondary flow portion N of the total fluid flow F is lower than the main flow portion H even in flushing mode.
  • the secondary flow portion N is increased compared to the conveying mode in order to enable thorough flushing of the secondary space 101.
  • the increased bypass flow proportion N is often not desired, since there is less need for flushing the adjoining space 101 and the increased bypass flow proportion N can negatively influence the delivery capacity of the gear pump 1.
  • the means 102 In order to be able to prevent fluid from flowing through the flushing channel 106 into the adjacent space 101 during conveying operation, analogous to the flushing operation, the means 102 therefore also have a closing device 107 for closing the flushing channel 106.
  • the design of the locking device 107 is described below based on the illustrations in Fig. 26 and 27 explained.
  • the closing device 107 is designed and arranged in such a way that flow through the flushing channel 106 is only possible in flushing mode. This can ensure that the increased secondary flow share N only is in flushing mode and the conveying operation is not affected.
  • the closing device 108 is arranged at the gear-side end of the flushing channel 106, but can alternatively also be arranged at the adjacent room-side end or in other sections of the flushing channel 106.
  • the closing device 107 has a closing element 108, which is movably mounted and is designed such that it can automatically close and open the flushing channel 106.
  • the closing and opening can take place under the influence of the pressure of the flowing fluid.
  • the closing element 108 is designed as a ball.
  • the closing element 108 is designed in such a way that it closes the flushing channel 106 during conveying operation, cf. Fig. 27 . Due to the excess pressure prevailing in the gear space 35 in the area of the flushing channel 106, the closing element 108 is pressed onto a closing surface 111, see also Fig. 28b , and prevents the flow through the flushing channel 106 from the gear space 35.
  • the closing element 108 In conveying mode, however, the closing element 108 automatically lifts off from the closing surface 111 and opens the flushing channel 106, cf. also Fig. 29b .
  • the closing element 108 is lifted off the closing surface 111 due to the changed pressure conditions in the flushing operation.
  • the secondary space 101 is fed with flushing fluid through the outflow opening 104 and the annular gap 105, which flows from the flushing channel 106 into the gear space 35 and thereby lifts the closing element 108.
  • the closing element 108 lies in the open position of the closing device 107 on an end face of the gear 4.1, cf. Fig. 26 and 27 .
  • the flushing channel has a guide 112 for guiding the opening and closing movements of the closing element 108.
  • the guide 112 points for this purpose, guide surfaces which support the closing element 108 and prevent it from tilting or jamming, cf. also, for example Fig. 31b .
  • the closing device 107 is designed as a check valve for opening and closing the flushing channel 106.
  • the functionality of the means 102 for increasing the bypass flow proportion N in the flushing operation is described below based on the illustrations in the Fig. 28a and b as well as 29a and b explained.
  • the conveyor operation is shown and in Fig. 29a and b the flushing operation.
  • the fluid flow F and its division into main flow components H and secondary flow components N are shown schematically in a very simplified manner. Since the flow directions S 1 , S 2 of the fluid locally depend strongly on various parameters, such as the operating point of the gear pump 1, the properties of the fluid and also on the section plane under consideration, only exemplary, simplifying information on the fluid flow F is given below in order to achieve this Increasing the bypass flow proportion N in flushing operation must be explained in principle. In real operation of the gear pump 1, the flow directions S 1 , S 2 and flow paths can deviate depending on the different influencing factors.
  • Fig. 28a illustrates an exemplary funding operation.
  • the driven gear 4.1 which for reasons of clarity Fig. 28a is not shown, is driven to rotate clockwise via the intermediate shaft 14.
  • the fluid stream F therefore flows as shown in Fig. 28a essentially along the flow direction S 1 from left to right, from the inlet 31, not shown, to the outlet 32, also not shown, see also Fig. 24a .
  • a certain proportion of the fluid flows through the annular gap 105 into the adjacent space 101.
  • the fluid cannot flow through the flushing channel 106 because the closing device 107 is closed. That is, the closing element 108 lies against the closing surface 111 and closes the flushing channel 106.
  • the secondary flow portion N flows back into the gear space 35 and combines with the fluid flow F.
  • the outflow opening 104 is arranged in a wall of the gear space 35.
  • the outflow opening 104 is arranged as a round bore near the inlet 31, where there is usually a negative pressure during conveying operation. Since the outflow opening 104 is arranged below the driven gear 4.1, the outflow opening 104 can be closed by a tooth of the gear 4.1 when the gears 4.1, 4.2 are at a standstill. Since in this case there would no longer be a flow connection to the adjacent space 101 and in particular no fluid could flow back from the adjacent space 101 into the gear space 35, the outflow opening 104 has a channel-like mouth opening 113, the length of which is greater than the width of a tooth. Thus, regardless of the position of the gear 4.1, there is always a flow connection between the gear space 35 and the adjacent space 101 via the outflow opening 104.
  • Fig. 31a and b show that the flushing channel 106 is also arranged below the driven gear 4.1, but near the outlet 32. In this area there is a negative pressure during the flushing operation, so that the closing element 108 automatically lifts off from the closing surface 111 and opens the flushing channel 106.
  • Fig. 31b The guide 112 for the closing element 108 illustrates this.
  • the flushing channel 106 has two channel-like mouth openings 110 at its gear-side end. These mouth openings 110 are fluidly connected to a compensation space 109.
  • the gear pump 1 has two compensation spaces 109, which are designed as elongated, channel-like recesses in the wall of the gear space 35.
  • the compensation spaces 109 serve as so-called squeezing grooves or squeezing volumes and are arranged in the area of the gear space 35 in which the teeth of the gears 4.1 and 4.2 are in mutual engagement.
  • a A certain proportion of the fluid is squeezed between the teeth of the gears 4.1, 4.2. This can suddenly create high pressure peaks in the fluid, which act on the gears 4.1, 4.2 and their bearings.
  • the compensation spaces 109 are provided into which the fluid can flow when it is squeezed between the teeth.
  • the shape and position of the compensation spaces 109 can be adapted in particular to the size of the squeezed volume of the fluid.
  • one of the compensation spaces 109 is fluidly connected to the gear-side end of the flushing channel 106. This allows the fluid to flow back and forth between the flushing channel 106 and the compensation space 109.
  • FIG. 32 illustrates the position of the inlet 31 and outlet 32, the outflow opening 104, the flushing channel 106 and the compensation spaces 109 relative to the gears 4.1, 4.2.
  • the outflow opening 104 and the flushing channel 106 run essentially parallel to the axis of rotation D of the intermediate shaft 14, which enables easy demolding during the initial forming production of the housing of the conveyor unit 2 and in particular of the gear space 35.
  • the fluid flows in the gear space 35 from an inlet 31 to an outlet 32.
  • a secondary flow portion N of the fluid flow F flows through the annular gap 105 into the secondary space 101 and back through the outflow opening 104 into the gear space 35.
  • the flushing channel 106 is closed by the closing element 108.
  • the fluid flow F flows from the outlet 32 to the inlet 31 and the pressure conditions within the gear space 35 change.
  • the secondary flow portion N of the fluid flow F is increased by the closing element 108 opening the flushing channel 106. Therefore, the secondary flow flows through the outflow opening 104 and the annular gap 105 into the adjacent space 101 and back through the flushing channel 106 into the gear space.
  • the bypass flow portion N is increased in the flushing mode compared to the conveying mode, among other things, because the flushing channel 106 has a larger cross-sectional area than the outflow opening 104. Increasing the bypass flow portion N in the flushing mode improves the flushing of the adjacent space 101.
  • the gear pump 1 described above, the pump arrangement 100 and the method for conveying a fluid flow F with such a gear pump 1 are therefore characterized by improved hygiene properties both in the conveying and in the rinsing mode.

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

Claims (13)

  1. Pompe à engrenage servant au refoulement d'un flux de fluide (F), dont le sens d'écoulement (S1, S2) peut être inversé par commutation entre un fonctionnement de refoulement et un fonctionnement de rinçage, comportant deux roues dentées (4.1, 4.2) disposées dans un espace à roues dentées (35) et un espace auxiliaire (101) relié fluidiquement à l'espace à roues dentées (35), le flux de fluide (F) étant formé par une partie d'écoulement principale (H) s'écoulant à travers l'espace à roues dentées (35) et une partie d'écoulement auxiliaire (N) s'écoulant au moins partiellement à travers l'espace auxiliaire (101),
    caractérisée par
    des moyens (102) servant à l'augmentation de la partie d'écoulement auxiliaire (N) lors du fonctionnement de rinçage, lesquels présentent un canal de rinçage (106) pouvant être fermé, lequel s'étend entre l'espace à roues dentées (35) et l'espace auxiliaire (101), les moyens (102) présentant un dispositif de fermeture (107) servant à la fermeture du canal de rinçage (106), lequel dispositif de fermeture est réalisé et disposé de telle sorte qu'un écoulement à travers le canal de rinçage (106) n'est possible que lors du fonctionnement de rinçage.
  2. Pompe à engrenage selon la revendication 1, caractérisée en ce que les roues dentées (4.1, 4.2) sont reliées fonctionnellement à une unité d'entraînement (3) par le biais d'un arbre intermédiaire (14).
  3. Pompe à engrenage selon la revendication 1 ou 2, caractérisée en ce que des composants de l'unité d'entraînement (3) sont disposés dans un espace d'entraînement (103), l'espace à roues dentées (35) étant disposé dans une région traversée par un écoulement de fluide et l'espace d'entraînement (103) étant disposé dans une région sèche, un joint d'étanchéité servant à la séparation étanche aux fluides de l'espace à roues dentées (35) vis-à-vis de l'espace d'entraînement (103) étant disposé dans l'espace auxiliaire (101).
  4. Pompe à engrenage selon la revendication 2 ou 3, caractérisée en ce que l'arbre intermédiaire (14) est rendu étanche par le biais d'une bague d'étanchéité d'arbre (15) dans l'espace auxiliaire (101).
  5. Pompe à engrenage selon l'une des revendications 2 à 4, caractérisée en ce qu'un palier lisse (17) servant au support de l'arbre intermédiaire (14) est disposé entre l'espace à roues dentées (35) et l'espace auxiliaire (101), la partie d'écoulement auxiliaire (N) s'écoulant au moins partiellement à travers un espace annulaire (105) réalisé dans la région du palier lisse (17).
  6. Pompe à engrenage selon l'une des revendications précédentes, caractérisée par une ouverture d'évacuation (104) reliant fluidiquement l'espace à roues dentées (35) à l'espace auxiliaire (101).
  7. Pompe à engrenage selon la revendication 6, caractérisée en ce que la partie d'écoulement auxiliaire (N) s'écoule le long d'un trajet d'écoulement auxiliaire lors du fonctionnement de refoulement, lequel trajet passe par l'interstice annulaire (105), l'espace auxiliaire (101) et l'ouverture d'évacuation (104).
  8. Pompe à engrenage selon la revendication 1, caractérisée en ce que le dispositif de fermeture (107) présente un élément de fermeture (108) monté mobile, lequel est réalisé et disposé de telle sorte que le dispositif de fermeture (107), lors de la commutation entre le fonctionnement de refoulement et le fonctionnement de rinçage, ouvre ou ferme automatiquement le canal de rinçage (106).
  9. Pompe à engrenage selon la revendication 8, caractérisée en ce que l'élément de fermeture (108), dans une position d'ouverture du dispositif de fermeture (107), s'appuie contre l'une des roues dentées (4.1, 4.2), en particulier contre un côté frontal de l'une des roues dentées (4.1, 4.2) et/ou, dans une position de fermeture, s'appuie contre une surface de fermeture (111) du canal de rinçage (106).
  10. Pompe à engrenage selon l'une des revendications précédentes, caractérisée en ce que l'espace à roues dentées (35) présente au moins un espace de compensation (109) servant à la compensation du volume d'écrasement des roues dentées (4.1, 4.2).
  11. Pompe à engrenage selon l'une des 5 à 10, caractérisée en ce que la partie d'écoulement auxiliaire (N) s'écoule le long d'un trajet d'écoulement auxiliaire lors du fonctionnement de rinçage, lequel trajet mène par le biais de l'ouverture d'évacuation (104) et de l'interstice annulaire (105) dans l'espace auxiliaire (101) et hors du canal de rinçage (106) ouvert dans l'espace à roues dentées (35).
  12. Pompe à engrenage selon l'une des revendications précédentes, caractérisée par une unité de refoulement (2) présentant les roues dentées (4.1, 4.2) et une unité d'entraînement (3) entraînant les roues dentées (4.1, 4.2), lesquelles sont reliées l'une à l'autre de manière libérable par le biais d'éléments de liaison (7, 8, 11, 12) pouvant être actionnés sans outil, les éléments de liaison (7, 8, 11, 12) étant réalisés sous forme d'éléments d'encliquetage.
  13. Procédé de refoulement d'un flux de fluide (F) à l'aide d'une pompe à engrenage (1) selon l'une des revendications 1 à 12,
    caractérisé en ce que la partie d'écoulement auxiliaire (N) est augmentée lors du fonctionnement de rinçage.
EP21216262.2A 2021-12-21 2021-12-21 Pompe à engrenage Active EP4202181B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DK21216262.2T DK4202181T3 (da) 2021-12-21 2021-12-21 Tandhjulspumpe
EP21216262.2A EP4202181B1 (fr) 2021-12-21 2021-12-21 Pompe à engrenage

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP21216262.2A EP4202181B1 (fr) 2021-12-21 2021-12-21 Pompe à engrenage

Publications (2)

Publication Number Publication Date
EP4202181A1 EP4202181A1 (fr) 2023-06-28
EP4202181B1 true EP4202181B1 (fr) 2024-03-13

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ID=78957822

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21216262.2A Active EP4202181B1 (fr) 2021-12-21 2021-12-21 Pompe à engrenage

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Country Link
EP (1) EP4202181B1 (fr)
DK (1) DK4202181T3 (fr)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4425226A1 (de) * 1994-07-16 1996-01-18 Abb Patent Gmbh Zahnradpumpe zur Lackförderung
DE19915784C2 (de) * 1999-04-08 2001-03-01 Fresenius Medical Care De Gmbh Zahnradpumpe, insbesondere für medizinische Zwecke
DE202006012407U1 (de) * 2006-08-12 2006-10-19 Industra Industrieanlagen - Maschinen Und Teile Gmbh Zahnradmaschine
DE102015109395A1 (de) * 2015-06-12 2016-12-15 AVS-Ing. J.C. Römer GmbH Selbstreinigende Pumpe
US10197054B2 (en) * 2017-02-13 2019-02-05 Bruno H. Thut Positive displacement transfer gear pump for molten metal

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EP4202181A1 (fr) 2023-06-28
DK4202181T3 (da) 2024-06-10

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