EP4170127A1 - Gear wheel pump - Google Patents

Abstract

The invention relates to a gear pump (1) for delivering a fluid, with a delivery unit (2) having at least two gears (4.1, 4.2) and a drive unit (3) which drives the gears (4.1, 4.2) and which can be actuated without tools via connecting elements (7, 8, 11, 12) are detachably connected to one another, the connecting elements (7, 8, 11, 12) being designed as latching elements. A further object of the invention is a pump arrangement (100) with such a gear pump (1) and at least one valve unit (18). A further object of the invention is a pump arrangement (100) with such a gear pump (1) and at least one valve unit (18). Another object of the invention is a method for detachably connecting a delivery unit (2) and a drive unit (3) of a gear pump (1) via connecting elements that can be actuated without tools.

Description

The invention relates to a gear pump for delivering a fluid, having a delivery unit having at least two gears and a drive unit driving the gears, which are detachably connected to one another via connecting elements that can be actuated without tools. Further objects of the invention are a pump arrangement with such a gear pump and at least one valve unit as well as a method for tool-free, detachable connection of the delivery unit and the drive unit of such a gear pump.

Gear pumps of this type are used in various areas of technology to convey fluids, in particular liquids, for example in vending machines or other systems in the food industry.

A gear pump usually has a delivery unit with two gears. The fluid to be conveyed is conveyed via the teeth of the gear wheels which are in mutual engagement and generate a pressure gradient along the conveying direction. A drive unit, which is connected to the conveyor unit and is often designed as an electric motor, is used to drive the gear wheels. The drive unit usually drives one gear directly and the other indirectly because of the meshing teeth. The delivery unit and the drive unit are often connected to one another via connecting elements that can be actuated without tools, which enables such gear pumps to be assembled and disassembled quickly or individual components such as the drive unit to be exchanged.

From the EP 3 282 086 A1 a gear pump for conveying a processing aid is known. The drive unit and the conveyor unit are detachably connected via separate connecting elements, which are designed as multi-part clamping rings. To connect the drive and conveyor unit, these are first aligned axially with one another, so that two flange-like clamping areas on the one hand of the drive unit and on the other hand of the conveyor unit lie flat against one another. The clamping rings are then placed manually around the flange-like clamping areas and clamped using an actuating element designed in the manner of a clamping screw with a wing nut. The actuating element is connected at one end in an articulated manner to the clamping ring and, for clamping, is folded into a position tangential to the clamping area, so that the wing nut engages behind a fork-shaped holding element. By subsequently turning the wing nut, the diameter of the clamping ring is reduced, whereby a clamping force in the radial direction is applied to the clamping area. The clamping rings have inclined surfaces so that the radial clamping force is converted into an axial connecting force in the area of the flange-like clamping areas and is used to connect the drive and delivery unit.

In practice, the use of separate, clamp-like clamping rings has proven to be disadvantageous in such gear pumps, since the use of such clamping rings is associated with a complex assembly process that requires several steps. Furthermore, the production of the connection via such clamping rings also depends to a certain extent on the skill of the fitter. This is because, as a result of incorrect positioning or insufficient clamping force, assembly errors can occur which can impair the operation of the gear pump or even lead to the gear pump failing.

Proceeding from this, the object of the invention is to specify a gear pump, a pump arrangement and a method which are characterized in that the delivery and drive unit of the corresponding gear pumps can be connected to one another in a simple and error-free manner.

In a gear pump of the type mentioned at the outset, this object is achieved by the features of patent claim 1 . Advantageous developments are specified in the dependent claims.

Due to the design of the connecting elements as latching elements, the drive unit is connected to the conveyor unit in a simple and error-free manner. In a user-friendly manner, the locking elements allow precise and repeatable assembly with a constant connection force, even after multiple loosening assembly personnel can be carried out safely. Assembly errors, which could result, for example, from incorrect positioning of the connecting elements or insufficient connecting force, are avoided.

In an advantageous embodiment, it is proposed that 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. It is particularly advantageous if the same number of connecting elements is formed on the conveyor unit and the drive unit. Furthermore, it is advantageous if the connecting elements on the conveyor unit and on the drive unit are designed to correspond in terms of their respective geometry. In addition, it has proven to be advantageous if the connecting elements are designed to correspond with respect to their respective position on the conveyor unit and the drive unit, which can result in a particularly simple possibility of connecting the drive unit to the conveyor unit. The connecting elements can be arranged directly on the conveyor unit and/or the drive unit. Alternatively, the connecting elements can also be arranged indirectly via an intermediate element on the conveyor unit and/or the drive unit. The intermediate element can optionally also have an adapter function, for example for arranging different drive units on one and the same conveyor unit.

In this context, it has proven to be particularly advantageous if the connecting elements are formed on sides of the conveyor unit and the drive unit that face one another. In this context, it can also be useful for connecting elements to be arranged on several sides of the conveyor and/or drive unit. This increases the flexibility with regard to the connection of the conveyor unit and drive unit with different alignments to each other.

An advantageous embodiment provides that connecting elements are formed on flat fastening areas of the conveyor unit and/or the drive unit. After locking the locking elements, there is a flat contact and thus a reliable connection.

Furthermore, it has proven to be advantageous if the connecting elements are arranged at equal distances, in particular angular distances, relative to one another. Such an arrangement allows the conveyor unit and the drive unit to be connected to one another in a simple manner and is also advantageous with regard to a uniform transmission of forces between the conveyor unit and the drive unit. As a result, a particularly high-quality and firm connection can be achieved between the conveyor unit and the drive unit. In this context, it is particularly preferred if the connecting elements are arranged at equal intervals relative to one another in the circumferential direction, as a result of which a particularly uniform connecting force can be generated.

It is also proposed that the connecting elements are designed in one piece with the conveyor unit and/or the drive unit. Such an arrangement is particularly advantageous with regard to a simple connection, since the connecting elements are designed to be captive. Furthermore, 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.

In an advantageous development of the invention, it is proposed that the conveyor unit and the drive unit can be connected to one another in a number of 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 just in one but in a number of 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, the accessibility to certain areas of the delivery unit and/or the drive unit can be improved in certain installation situations. Advantageously, two possible assembly positions can be provided for two pairs of connecting elements. Furthermore, with three pairs of connecting elements, three possible mounting positions can be provided, etc. It is particularly preferred if four mounting positions are provided and selectable with four pairs of connecting elements. Such an embodiment enables a quick and user-friendly connection of the drive unit to the conveyor unit, since it can already be determined from the number of pairs of connecting elements how many possible assembly positions there are.

In an advantageous development of the invention, it is proposed that the connecting elements form a bayonet connection. Such a bayonet connection is particularly advantageous with regard to a simple and error-free latching connection of the drive unit to the conveyor unit. Furthermore, a bayonet connection can be used by the assembly personnel enable intuitive, repeatable, non-destructively releasable locking connection of the drive unit with the conveyor unit. Establishing a connection via a bayonet connection can also be carried out easily and without error, even for inexperienced assembly personnel.

In this context, it is proposed that the connecting elements are designed as bayonet hooks and/or corresponding recesses. Such an embodiment enables a bayonet connection to be produced in a simple manner. In particular, it is 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.

In this context, it is also proposed that the bayonet hooks have an essentially rectangular shape with a base and a latching part that spreads out from the base at right angles. Such an arrangement allows a simple and assembly-friendly connection by means of the bayonet connection. In addition, the latching part that spreads out at right angles from the base can be used in a simple manner to produce a high-quality, form-fitting latching connection. As an alternative to the right-angled spread, transverse spreads of the latching part from the base can also be provided in an angular range of 80° to 100° to the base.

In this context, it has proven to be structurally advantageous if the latching part points radially outwards or radially inwards.

It has also proven to be structurally advantageous if the recesses have an insertion area for inserting the bayonet hooks and a securing area for latching the bayonet hooks.

In this context, it is also proposed that the securing area for latching be designed to interact with the latching part of the bayonet hook. Such an embodiment enables a user-friendly connection between the drive unit and the delivery unit, which is reliable even if it is released several times, by means of a bayonet connection.

In a structurally advantageous embodiment, the recesses are designed as circular ring segments, with the plug-in areas extending over one half of the circular ring segments and the securing areas being arranged in the other half of the circular ring segments. It is preferred if the geometry of the plug-in areas is designed to correspond to the geometry of the bayonet hooks, and in particular the locking part of the bayonet hooks. Furthermore, such an arrangement can be advantageous with regard to user-friendly assembly of the conveyor unit and drive unit. The production of a bayonet connection can be made possible in an advantageous manner by sequentially inserting the bayonet hooks into the insertion area of the recesses and then rotating the bayonet hooks relative to the recesses. As a result, the locking part of the bayonet hook can be locked in a form-fitting manner with the securing area of the recesses. As an alternative to an extension over half of the circular ring segments, extensions over a proportion of between 30% and 70% and in particular 40% and 60% of the width of the circular ring segments can also be provided. In this context, adapted to the requirements of the connection between the conveyor unit and the drive unit, other geometric relationships, in particular wider or also less wide plug-in areas, are also conceivable.

In this context, it is also proposed that the securing areas extend in a flat and web-like manner from the outer radius of the circular ring segments in the radial direction over at least one third of the extent of the circular ring segments extend. As an alternative to extending over a third of the radial extent, the securing areas can also extend by 10% to 50% and in particular 25% to 45% of the radial extent of the circular ring segments.

In a development of the invention, it is proposed that the securing areas have a compensating ramp for tolerance compensation, which is designed to interact with the latching parts of the respective bayonet hooks. Such an embodiment enables tolerances to be compensated for and a play-free locking connection of the conveyor unit with the drive unit in a simple and advantageous manner. The compensating ramp is preferably designed in such a way that it can be reversibly deformed when tolerances overlap.

In this context, it is also preferred if the compensating ramp is arranged on the securing area as an inclined plane rising in the circumferential direction of the circular ring segment, which extends in particular over at least two thirds of the length of the securing area. Such a configuration of the compensating ramp enables a simple and user-friendly tolerance compensation. Depending on the relative position of the locking part of the bayonet hook to the compensation ramp of the security area, different tolerances can be compensated. The inclined plane can have a constant angle of rise or one that varies over the length of the compensating ramp. The individual security areas can have compensating ramps of the same design.

It is further proposed that the drive unit and the conveyor unit are designed to be rotatable in relation to one another about an axis of rotation in order to fix or release the bayonet connection. In an advantageous manner, the drive unit and the delivery unit can initially be plugged into one another in the axial direction along the axis of rotation in the area of the connecting elements and in a second step are rotated relative to each other about an axis of rotation against each other. This allows a snap-in connection of the drive unit to the conveyor unit that can be established quickly and reliably even by inexperienced operating personnel. Furthermore, such a connection can be broken in a simple manner in a non-destructive manner by reversing the process steps carried out for the connection.

In this context, it is further proposed that the axis of rotation corresponds to the drive axis of the drive unit. This enables an axially symmetrical structure, in which case the drive unit and/or the conveyor unit can be rotated about the drive axis for connection. Advantageously, the connection can be made by turning in one direction of rotation and the connection can be released by turning in the opposite direction of rotation.

In a development of the invention, it is proposed that the conveyor unit has at least two bayonet hooks and the drive unit has at least two corresponding recesses for engaging the bayonet hooks. Such an arrangement is advantageous with regard to a simple connection between the delivery unit and the drive unit which is uniform in terms of the connection force. In this context, it can alternatively also be advantageous that the conveyor unit has at least two recesses and the drive unit has at least two corresponding bayonet hooks.

In a development of the invention, it is proposed that 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. In this connection it is of particular advantage if the bayonet hook and the corresponding Recesses are arranged in a circle and evenly over the circumference. It is also easily conceivable that 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.

In a development of the invention, it is also proposed that the bayonet connection has a reverse rotation lock. Such an embodiment is advantageous for securing against unintentional loosening of the connection. Furthermore, a reverse rotation lock can secure the delivery unit and the drive unit against an undesired loosening of the connection as a result of shocks and/or vibrations that can occur during operation of the gear pump. As a connection indicator, the anti-reverse device can also indicate a correct connection between the drive unit and the conveyor unit.

In this context, it has proven to be advantageous if the anti-reverse device has at least one spring-loaded safety hook, which interacts with at least one corresponding safety recess in a form-fitting manner. Such a design enables the connection to be secured against turning back easily and securely. It is particularly advantageous in this connection if the securing hook is designed to be resilient in the radial direction. Furthermore, the securing recess can advantageously be adapted to the structural design of the securing hook in terms of its position and geometric shape.

In this context, it is also proposed that the safety hook has a safety lug for engagement in a corresponding safety recess having. Such a safety lug allows a simple and effective reverse rotation lock. In particular, it can be advantageous if the geometry of the securing lug is adapted to the geometry of the corresponding securing recess.

In this context, it has proven to be structurally advantageous if 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. With such an arrangement, the conveyor unit and the drive unit can be secured in a simple and reliable manner against unintentional turning back and thus against unintentional loosening of the connection. It is also conceivable in this connection for the drive unit to have a safety hook, which is designed to interact with at least one safety recess arranged on the conveyor unit to prevent reverse rotation.

In this context, it is also proposed that the anti-reverse device has a safety hook and a plurality of safety recesses, in which the safety hook can engage depending on the mounting position. Such an arrangement enables the conveyor unit and the drive unit to be connected in a number of assembly positions, and these can be secured against unintentional turning back. It has proven to be advantageous if the drive unit has at least two, preferably four and particularly preferably as many securing recesses around the circumference as there are connecting elements on the drive unit or on the conveyor unit. Furthermore, it is easily conceivable that 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 latching connection of the drive unit to the conveyor unit.

In this context, it is proposed that the connecting elements be designed as resilient latching tongues and/or corresponding recesses. In particular, the latching tongues can be designed in such a way that they can be inserted in a form-fitting manner into the corresponding recesses. With regard to a simple connection, it has proven to be advantageous if the latching tongues are designed to be radially resilient.

In this context, it is also proposed that the latching tongues have a latching area which is designed to interact in a form-fitting manner with a corresponding latching area of the recesses. Such a construction allows a simple and error-free latching connection between the conveyor unit and the drive unit. The latching connection can be created by simply inserting the latching tongues into the corresponding recesses.

In addition, it is proposed that the latching tongues have an insertion bevel for easy insertion into the recesses. This achieves a user-friendly design of the latching tongues. In this case, the insertion bevel can be designed as an inclined plane extending from the tip of the latching tongues in their axial direction. In this case, the edge of the recesses can be designed to interact with the insertion bevel and support springing in of the latching tongues.

It is also proposed that the latching tongues be designed in such a way that when they are inserted, they compress the recesses transversely to their insertion direction and spring out when the connection position is reached, as a result of which the latching areas latch with one another. Such a construction is advantageous with regard to a simple connection of the drive unit to the delivery unit by plugging in in the axial direction. Furthermore, the latching areas latched to one another can also serve as an indicator of a successful connection of the delivery unit to the drive unit. For this purpose, the latching tongues can have markings of a different color, in particular at their tip, as a connection indicator, which are arranged visibly when latched correctly and indicate a successful connection. Assembly errors can be avoided in this way.

In this context, it is also proposed that the latching tongues be designed in such a way that they deflect transversely to the direction of insertion when a releasing force applied counter to the direction of insertion is reached. Such a design enables the connection to be released easily. By applying the releasing force, the locking can be canceled in a simple manner. In a particularly advantageous manner, the releasing force to be applied for releasing is selected in such a way that it cannot easily occur during operation of the gear pump, as a result of which an unintentional release of the snap hook connection during operation can be prevented.

It is further proposed that the conveyor unit has at least two latching tongues and the drive unit has at least two corresponding recesses for engaging the latching tongues. This has proven to be advantageous with regard to a safe, symmetrical and resilient connection between the conveyor unit and the drive unit. It is also conceivable in this context that the drive unit has at least two Locking tongues and the conveyor unit has at least two corresponding recesses for engagement of the locking tongues.

It has also proven to be advantageous if the conveyor unit has three, four or five latching tongues for connection to three, four or five corresponding recesses arranged on the drive unit. Such an arrangement is of particular advantage for the mechanical strength of the connection between the conveyor unit and the drive unit. It is particularly advantageous if the three, four or five locking tongues or the three, four or five corresponding recesses are arranged in a circle at a uniform distance from one another on the respective fastening area. It is also easily conceivable that the drive unit can have three, four or five latching tongues for connection to three, four or five corresponding recesses arranged on the conveyor unit.

In a development of the invention, guide elements are proposed for guiding the plug-in movements when connecting and/or releasing the snap hook connection. Such guide elements can simplify the production of the locking connection between the conveying element and the drive element. Furthermore, such 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.

It can also be advantageous if the connecting elements are formed on at least one intermediate element, with the intermediate element being fastened to the conveyor unit and/or the drive unit. When using such an intermediate element, the connecting elements are indirectly connected to the drive unit and/or the conveyor unit via the intermediate element. The intermediate element can be in the form of an adapter be adapted to the requirements of the connection between the conveyor unit and the drive unit. Different drive units and conveyor units can therefore also be connected to one another by using different intermediate elements. This can be an advantage, for example, when replacing a less powerful drive unit with a more powerful one. The intermediate element can be designed in the manner of a disc. 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. It has also proven to be advantageous if the intermediate element is detachably attached to the conveyor unit and/or the drive unit. In particular, a detachable attachment by means of attachment means such as screws or bolts may be preferred. Such an arrangement can enable the intermediate element to be changed easily and quickly. Furthermore, the intermediate element can thus be exchanged in a simple manner. However, the intermediate element can also be non-detachably fastened to the conveyor unit and/or the drive unit if this turns out to be advantageous for the respective application.

It is of structural advantage if the drive unit for driving the gear wheels is operatively connected to the gear wheels via an intermediate shaft. Such a design enables the drive unit to be replaced quickly and easily.

It has proven to be advantageous if the intermediate element has a shaft bearing for supporting the intermediate shaft. Such an arrangement enables reliable mounting of the intermediate shaft in a simple manner. The shaft bearing is preferably in the middle and after Kind of a cylindrical collar formed on a substantially disc-shaped intermediate element.

In this context it is proposed that the shaft bearing has a shaft sealing ring for sealing the intermediate shaft. Such a shaft sealing ring enables the intermediate shaft to be sealed off in a simple manner. Furthermore, the position of the shaft sealing ring can be specified in a simple manner by such an arrangement.

In an advantageous embodiment, the intermediate shaft has an actuating contour which can be positively connected to a corresponding actuating contour arranged on at least one of the gearwheels. In this way, the intermediate shaft and the gear wheel can be connected to one another in a simple and user-friendly manner. This gear is a driven gear.

It is also proposed that at least one of the gears has a bearing contour for freely rotatable arrangement on a bearing axle. Such a bearing contour has proven to be advantageous for mounting the gear wheel on the bearing axle. This gear is a co-rotating gear.

In this context, it is further proposed that the actuating contours can be connected to one another in a form-fitting manner. In particular, it is advantageous if the actuating contour of the intermediate shaft is designed to correspond to the actuating contour of at least one of the gearwheels and can be connected to it in a form-fitting manner. Such a configuration enables a simple form-fitting connection of the intermediate shaft to at least one of the gears. It is particularly advantageous if the driven gear wheel of the gear pump has an actuating contour.

In addition, it is proposed that the actuating contour of the intermediate shaft should not be designed so that it can be inserted into the bearing contour. Such a configuration makes it possible for the intermediate shaft not to be able to be connected to the non-driven gear wheel, which has the bearing contour. This also makes it possible to avoid assembly errors, since the intermediate shaft can only be connected to the driven gear intended for this purpose.

It is proposed that the actuating contours be designed in the manner of a polygon, in particular a pentagon. Such a configuration has proven to be advantageous with regard to low-loss power transmission. Furthermore, a polygon can be produced in a simple manner. In particular, a polygon can be designed as the outer contour of a bolt or as the inner contour of a bore.

In this context, it has proven to be advantageous if the bearing contour is designed as a round bore. Such a round bore allows a simple, freely rotatable mounting of the non-driven gear wheel on the bearing axle.

With regard to simple assembly, it is advantageous if the diameter of the round bore and the diameter of the polygon of the actuating contour are selected in such a way that they cannot be plugged into one another. This enables the gear pump to be assembled in a simple and error-free manner. Assembly errors due to incorrect connection of the intermediate shaft and/or the bearing axle to the gears can be prevented.

In addition, it is proposed that the conveyor unit has a sliding bearing for supporting the intermediate shaft of the drive unit. In this context, it has proven to be advantageous if the sliding bearing located near the driven gear. Such a constructive arrangement can reduce friction and wear, since angular errors between the intermediate shaft and the gear wheel can be compensated for by the slide bearing.

It has proven to be structurally advantageous if the gears are arranged in a gear space delimited by a wall of the conveyor unit and the plain bearing is arranged in the wall. In such an embodiment, the plain bearing is in close proximity to the gears. Angular errors are effectively compensated.

It is also proposed that the gear pump has a connection indicator showing the connection between the delivery unit and the drive unit. With correct latching, this connection indicator can be arranged so that it is visible to the assembly personnel and can indicate a successful connection. Assembly errors can be avoided in this way.

In this context, it is structurally proposed that the connection indicator is formed on the anti-reverse lock of the bayonet connection and/or on the latching tongue of the snap hook connection.

In addition, a pump arrangement with a gear pump and at least one valve unit according to patent claim 14 is proposed to solve the above-mentioned problem. The same advantages mentioned above in relation to the gear pump result in connection with the pump arrangement. Such a pump arrangement advantageously enables the fluid flow to be controlled.

In this context, it is proposed that the delivery unit of the gear pump be connected to a valve unit via connecting elements that can be actuated without tools connected is. Such a design enables a quick and user-friendly connection between the delivery unit and the valve unit.

In this context, it has proven to be advantageous if the connecting elements are designed as latching elements. This results in the same advantages that have already been explained above with regard to the connection between the conveyor unit and the drive unit.

It is particularly preferred if the connecting elements form a bayonet connection. In particular, it is advantageous if the bayonet connection is designed in accordance with the bayonet connection described above.

Alternatively, the connecting elements can also form a snap hook connection. In particular, it is advantageous if the snap hook connection is designed in accordance with the snap hook connection described above.

In addition, a method according to patent claim 15 is proposed to solve the above-mentioned problem. The same advantages mentioned above in relation to the gear pump and the pump arrangement result in connection with the method. In particular, such a method enables the conveyor unit to be connected to the drive unit in a simple and error-free manner.

In connection with the method, it is proposed that the gear pump be designed according to one or more of the features described above.

Fig. 1 und 2

perspektivische Ansichten einer erfindungsgemäßen Zahnradpumpe gemäß einer ersten Ausführungsform;

Fig. 3

eine Schnittdarstellung der Zahnradpumpe gemäß der Darstellung in Fig. 2;

Fig. 4

eine perspektivische Explosionsansicht der Zahnradpumpe gemäß Fig. 3;

Fig. 5

einen Querschnitt der Zahnradpumpe im Bereich der Fördereinheit;

Fig. 6a bis 6c

perspektivische Ansichten der Zahnräder sowie einer Zwischenwelle der Zahnradpumpe;

Fig. 7

eine schematische Darstellung der Betätigungs- und Lagerkontur;

Fig. 8a

eine perspektivische, teilweise geschnittene Ansicht einer Zahnradpumpe;

Fig. 8b

eine vergrößerte Ansicht der in Fig. 8a mit VIII b bezeichneten Einzelheit;

Fig. 9a bis 9e

perspektivische Ansichten der Bajonettverbindung einer Zahnradpumpe;

Fig. 10 und 11

perspektivische Ansichten zur Veranschaulichung des Toleranzausgleichs der Bajonettverbindung einer Zahnradpumpe;

Fig. 12a

eine Schnittansicht der Bajonettverbindung gemäß Fig. 10;

Fig. 12b

eine Schnittansicht gemäß der in Fig. 12a mit XII b bezeichneten Einzelheit;

Fig. 13

eine perspektivische Detailansicht der Bajonettverbindung gemäß Fig. 11;

Fig. 14

eine weitere perspektivische Detailansicht der Bajonettverbindung gemäß Fig. 11;

Fig. 15 bis 17

perspektivische Ansichten einer Zahnradpumpe gemäß einer zweiten Ausführungsform;

Fig. 18 bis 20

Detailansichten der Schnapphakenverbindung der Zahnradpumpe gemäß Fig. 15 bis 17; und

Fig. 21 bis 23

perspektivische Ansichten verschiedener Pumpanordnungen mit einer Zahnradpumpe und mehreren Ventileinheiten.

Further details and advantages of the invention are explained below with the aid of the accompanying drawings of exemplary embodiments. However, the invention is not limited to these exemplary embodiments. Further exemplary embodiments can result from combining the features of one or more of the features described above with one another and/or with one or more features of the exemplary embodiments or claims. In the drawings show:

Figures 1 and 2

perspective views of a gear pump according to the invention according to a first embodiment;

3

a sectional view of the gear pump as shown in FIG 2 ;

4

an exploded perspective view of the gear pump according to FIG 3 ;

figure 5

a cross section of the gear pump in the area of the delivery unit;

Figures 6a to 6c

perspective views of the gears and an intermediate shaft of the gear pump;

7

a schematic representation of the actuation and storage contour;

Figure 8a

a perspective, partially sectioned view of a gear pump;

Figure 8b

an enlarged view of the in Figure 8a item marked VIII b;

Figures 9a to 9e

perspective views of the bayonet connection of a gear pump;

Figures 10 and 11

perspective views to illustrate the tolerance compensation of the bayonet connection of a gear pump;

12a

a sectional view of the bayonet connection according to FIG 10 ;

Figure 12b

a sectional view according to FIG 12a item marked XII b;

13

a detailed perspective view of the bayonet connection according to FIG 11 ;

14

a further detailed perspective view of the bayonet connection according to FIG 11 ;

Figures 15 to 17

perspective views of a gear pump according to a second embodiment;

Figures 18 to 20

Detailed views of the snap hook connection of the gear pump according to Figures 15 to 17 ; and

Figures 21 to 23

perspective views of different pump arrangements with a gear pump and several valve units.

The depictions in the 1 and 2 show a gear pump 1 with a delivery unit 2 for delivering 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, via two connections 26 serving as inlet and outlet, from the fluid to be delivered, in which it can be drinking water, for example, can be flown through.

The drive unit 3 is detachably connected to the conveyor unit 2 . For this purpose, several connecting elements 7, 8 are provided. The connecting elements 7, 8 are designed as locking elements and therefore allow a simple and error-free locking connection of the conveyor unit 2 and the drive unit 3.

The latching elements 7, 8 face one another and act together in a latching manner in the manner of a bayonet connection 50, cf. 2 . Details of the bayonet connection 50 are based on the representations in the 9a to 14 be explained in more detail.

The connecting elements 7 are arranged on an end face of the conveyor unit 2 and interact with the connecting elements 8 arranged on the drive unit 3 in a latching manner. While the connecting elements 7 are arranged directly on the conveyor unit 2 , the connecting elements 8 are arranged indirectly on the drive unit 3 via a disc-shaped intermediate element 6 . The indirect arrangement of the connecting elements 8 on the drive unit 3 has the advantage that the intermediate element 6 can be used as an adapter for connecting different drive units 3, e.g.

Alternatively, it would also be conceivable for the connection elements 8 on the drive side to be arranged directly on the drive 3 . It would also be conceivable for the connecting elements 7 to be formed on an intermediate element, which is not shown in the figures and is connected to the conveyor unit 2 .

While the representation in 1 shows a disconnected state, shows the representation in 2 the mounted gear pump 1, in which the drive unit 3 and the delivery unit 2 are detachably connected to one another via the bayonet connection 50 by mutual latching. In the assembled state, 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.

Details of the drive unit 3, the intermediate element 6 and the conveyor unit 2 are described below, in particular with reference to the illustrations in FIGS Figures 3 and 4 explained.

The drive unit 3 of the gear pump 1 has a substantially cylindrical geometry and is designed as an electric motor. The drive unit 3 has electrical connections 3.1. By energizing the drive unit 3, a drive shaft 3.2 is set in rotation, which is used to drive the conveyor unit 3.

In the exemplary embodiment, the drive unit 3 is a commercially available standard electric motor in a wide variety of designs, such as brushless or brushed electric motors of different power classes. In order to transmit the rotational movement of the drive unit 3 generated by the drive unit 3 to the conveyor unit 2 , 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. On one side, the intermediate shaft 14 is connected to a drive shaft 3.2, designed as a short stub axle, of the drive unit 3 and on the other side to the conveyor unit 3. Alternatively, it would also be conceivable for the intermediate shaft 14 to be connected in one piece to the drive shaft 3.2. In this case, however, a standard motor could not be used.

As is shown, for example, in the illustration in 4 becomes clear, 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 chrome content of 16%, which is approved for use in the food sector or for driving gear pumps 1 for pumping drinking water. The drive shaft 3.2 of the drive unit 3 does not come into contact with the fluid to be pumped due to the intermediate shaft 14 pressed on in the manner of a shaft extension.

On one end face, the drive unit 3 has a disc-shaped intermediate element 6 which is releasably attached to the drive unit 3 by means of 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 . In addition, 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 center of the intermediate element 6 essentially perpendicularly 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 plug-in connection elements 22 shaped like dumbbells. The plug-in connection elements 22 are inserted into correspondingly designed recesses 33 for connection and overlap the planar contact area between the housing 2.1 and the cover 2.2 on its underside and upper side, see 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, not shown, components of the respective hydraulic system. On the side opposite the connections 26, the delivery 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 1 designed as a bayonet hook. In the present exemplary embodiment, the bayonet hooks 7 are arranged directly on the fastening area B. Alternatively, however, it is also conceivable for these to be arranged indirectly on the fastening area B via an intermediate element 6 . An inverse arrangement would also be conceivable, ie arranging the bayonet hooks 7 on the drive side and the recesses 8 on the conveying 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 on it are preferably made of plastic by means of suitable methods, in particular injection molding methods. All components that come into contact with the fluid to be pumped are suitable for use in the food and drinking water sectors.

Below is the arrangement of the gears 4.1 and 4.2 in the conveyor unit 2 and their drive based on the illustrations in the Figures 3 to 7 explained in more detail.

A gear space 35 is arranged inside the housing 2.1. The gear space 35 is sealed off from the cover 2.2 by means of a seal 25 designed as an O-ring. In the gear space 35 two gears 4.1 and 4.2 are rotatably arranged. The teeth of the driven gear 4.1 engage in the corresponding gaps in a second co-rotating gear 4.2. The co-rotating gear 4.2 is rotatably mounted parallel to the axis of the driven gear 4.1 on an axle 21 arranged in the housing 2.2. Both gears 4.1, 4.2 are flowed around by the fluid to be pumped. A rotating movement of the driven gear wheel 4.1 causes the co-rotating gear wheel 4.2 to rotate in the opposite direction. This creates a pressure gradient that can be used to convey the fluid, via which the fluid flows from an inlet 31 to an outlet 32 . The connections 26 are connected to the inlet 31 and the outlet 32 and can be guided through the cover 2.2 or arranged on the lateral walls of the housing 2.1.

The driven gear wheel 4.1 is plug-connected to the intermediate shaft 14 for driving the conveyor unit 2. The drive force is transmitted from the intermediate shaft 14 to the driven gear wheel 4.1 via corresponding actuating contours 14.1 and 16.1. In the present exemplary embodiment, 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. Figure 6c . The driven gear wheel 4.1 has a corresponding pentagonal contour, designed as an inner contour, as the actuating contour 16.1, cf. Figure 6b . The actuating contour 14.1 is inserted into the actuating contour 16.1 to drive the driven gear wheel 14.1. The design as a pentagon enables the torque to be transmitted effectively.

In order to prevent a possible incorrect assembly of the intermediate shaft 14 on the co-rotating gear wheel 4.2, the co-rotating gear wheel 4.2 has no actuating contour, but rather a bearing contour 16.2 designed as a round bore, cf. Figure 6a . The geometries of the actuating contour 14.1 and the bearing contour 16.2 are selected in such a way that the actuating contour 14.1 of the intermediate shaft 14 cannot be inserted into the bearing contour 16.2 of the co-rotating gear wheel 4.2, cf. 7 . This ensures that the intermediate shaft 14 can only be connected to the driven gear 4.1. The bearing contour 16.2 is designed in such a way that the co-rotating gear wheel 4.2 can only be connected to the corresponding axle 21 provided for this purpose, see also FIG Figure 8b .

A shaft sealing ring 15 is provided to seal the intermediate shaft 14 from the gear space 35 arranged in the housing 2.1 of the delivery unit 2, cf. 4 . In the present exemplary embodiment, the shaft sealing ring 15 is designed as a radial shaft sealing ring. In order to achieve the hardness of the intermediate shaft 14 of at least 45 HRC required for sealing with the shaft sealing ring 15, 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 Kolsterizing. In order to prevent the risk of damage to the shaft sealing ring 15 during assembly, the edges of the operating contour 14.1, which is designed as a pentagon, are rounded.

Based on the illustrations in the Figures 8a and 8b the storage of the gears 4.1 and 4.2 in the conveyor unit 2 is explained below. Figure 8b shows an enlargement of section VIII b according to FIG Figure 8a .

As previously explained, the driven gear wheel 4.1 is slipped onto the actuating contour 14.1 of the intermediate shaft 14. A slide bearing 17 in the housing 2.1 of the conveyor unit is in the immediate vicinity of the gear wheel 4.1 2 arranged. The arrangement of the slide bearing 17 in the wall 2.3 of the conveyor unit 2 near the gear wheel 4.1 enables additional guidance of the intermediate shaft 14. The slide bearing 17 can be designed as a recess in the wall 2.3 if the wall is made of a suitable material. Alternatively, the plain bearing 17 can be used as a separate component in the wall 2.3 and be 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 from the plain bearing 17, can be reduced in the area of the gear wheel 4.1. This enables the gear pump 1 to run smoothly, which can also reduce the wear on the gear wheels 4.1 and 4.2. In a similar way, the axis 21 of the co-rotating gear wheel 4.2 is also mounted in the area of this gear wheel 4.2 by means of a plain bearing. The sliding bearing of the co-rotating gear 4.2 can also be used in one piece on the gear 4.2 or as a separate sliding bearing in this.

The following is based on the representations in the 9a to 14 the configuration of the bayonet connection 50 provided in the first exemplary embodiment is explained.

The representation in Figure 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 point of the fastening area B. FIG. The bayonet hooks 7 are arranged point-symmetrically to a central round bore of the fastening area B at regular intervals, so that there is an angle of 90° between the bayonet hooks 7 in each case. The bayonet hooks 7 are formed in one piece with the housing 2.1. Based on the representation in 14 it can be seen that the bayonet hooks 7 are essentially L-shaped with a rectangular base area and have a base 7.1 and a latching part 7.2. The Base 7.1 extends perpendicularly from the surface of the attachment area B. At a certain distance from the surface of the attachment area B, the latching 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 facilitate insertion into the corresponding recesses 8.

As explained, the intermediate element 6 fastened to the drive unit 3 in the present exemplary embodiment is designed in the manner of a flat round disk, cf. Figure 9b . The intermediate element 6 has four continuous recesses 8 which are designed in the manner of circular ring segments 34 . The recesses 8 are designed in such a way that they can interact with the bayonet hooks 7 to connect the delivery 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 spacing of the recesses is accordingly 90°.

The recesses 8 each have a plug-in area 8.1, cf. 10 . This plug-in area 8.1 is adapted to the geometry of the locking part 7.2 of the bayonet hook 7 and enables the bayonet hook 7 to be inserted . This securing area 8.2 is designed to interact with the latching part 7.2 of the bayonet hook 7. It extends flat and web-like from the outer radius of the recess 8 to about one third of its radial length, cf. 10 . The securing area 8.2 is arranged in the lower area of the recess 8; its thickness corresponds to approximately half the thickness of the intermediate element 6, cf. 12a . The recesses 8 have bevels for easy connection to the bayonet hooks 7 .

In order to establish the connection by means of the bayonet connection 50, the conveyor unit 2 and the drive unit 3 are configured such that they can be rotated relative to one another, with the axis of rotation D corresponding to the drive axis A, see also FIG 3 . As a result of the mutual twisting, the securing area 8.2 of the recess 8 and the latching part 7.2 of the bayonet hook 7 come into mutual engagement, cf. 12a . No additional tools are required to produce the bayonet connection 50 . In the connected state according to 11 the four bayonet hooks 7 grip behind the securing areas 8.2 of the recesses 8, as a result of which they are locked in a form-fitting manner.

In order to prevent the connection from being released unintentionally or accidentally, the bayonet connection 50 has a reverse rotation lock 10 for securing against reverse rotation. In particular, the anti-reverse device 10 serves to secure against undesired loosening due to vibrations or shocks during operation of the gear pump 1. For this purpose, the delivery unit 2 has a safety hook 10.1, cf. Figure 9a . The safety hook 10.1 is arranged radially on the outside of the fastening area B and is designed as a spring arm which is articulated on one side and is resilient in the radial direction. Furthermore, the safety hook 10.1 has a projecting safety lug 10.2, which extends essentially perpendicularly to the surface of the fastening area B at the free end of the safety hook 10.1. In the correctly assembled state, the securing lug 10.2 engages in a correspondingly designed recess 10.3 of the intermediate element 6, cf. Figures 9d and 9e . To release the bayonet connection 50, the safety hook 10.1 can be manually disengaged from the recess 10.3. Alternatively or additionally, a releasing force sufficient to release the bayonet connection 50 can be generated by mutually rotating the delivery unit 2 relative to the drive unit 3 .

The reverse rotation lock 10 has a dual function. It not only serves to avoid unintentional loosening, but also shows a correctly latched bayonet connection 50 between the conveyor unit 2 and the drive unit 3 as a connection indicator 36 that can be read from the outside. Only when the bayonet connection 50 is correctly engaged are the securing lug 10.2 visible from the outside and the recess 10.3 engaged with one another.

In the exemplary embodiment, the intermediate element 6 has a total of four recesses 10.3, which are arranged at equal distances over the circumference of the intermediate element 6, cf. Fig. 9e . 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.

Furthermore, the securing areas 8.2 each have a compensation ramp 9 for tolerance compensation. The compensating ramp 9 is designed in such a way that it can interact with the latching part 7.2 of the corresponding bayonet hook 7. The compensating ramp 9 is arranged in the circumferential direction over about two thirds of the length of the securing area 8.2 and essentially covers its entire width in the radial direction. The compensating ramp 9 is designed as an inclined plane that rises in the circumferential direction and, in the installed state, extends in the direction of the latching part 7.2 of the bayonet hook 7, see also FIG Figure 12b . Together with the locking part 7.2 of the bayonet hook 7, the compensating ramp 9 can be used to compensate for tolerances and ensure a play-free connection between the conveyor unit 2 and the drive unit 3. For this purpose, the compensating ramp 9 is designed in such a way that it can be reversibly deformed if there is a tolerance overlap.

The depictions in the Figures 15 to 20 show a second embodiment which, in contrast to the first embodiment, does not have a bayonet connection 50 but a snap hook connection 60, but otherwise corresponds to all relevant features of the first embodiment.

The snap hook connection 60 differs from the bayonet connection 50 described above essentially in the structural design of the connecting elements 11, 12.

The representation in 15 1 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 point of the fastening area B. FIG. The recesses 12 are arranged at equal 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 in each case. The recesses 12 are designed as essentially rectangular openings in the attachment area B, cf. 19 . The recesses 12 each have a latching area 12.1, which is arranged in the manner of an edge on the back of the fastening area B, see also FIG 20 . Between the recesses 12 further, also rectangular openings are arranged on the fastening area B. Furthermore, 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.

Similar to the first embodiment, four latching tongues 11 of the snap hook connection 60 are formed on an intermediate element 6, cf. 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 designed as a cylindrical collar. The latching tongues 11 are designed to be resilient in the radial direction in the manner of a resilient cantilever. The four latching 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 produce a latching connection, cf. 16 . In the region of their tip, the latching tongues 11 have a latching area 11.1, which is designed like an edge transversely to the tab-like base body of the latching tongue 11. The tip of the latching tongues 11 is provided with an insertion bevel 11.2, by means of which the insertion of the latching tongues 11 into the corresponding recesses 12 of the conveyor unit 2 can be facilitated. Furthermore, 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 latching tongues 11.

To produce the snap hook connection 60, the drive unit 3 is moved in the insertion direction R along the drive axis A toward the conveyor unit 2 and inserted into the recesses 12, cf. Figures 15 and 16 . When plugging in, the tips of the snap-in tongues 11 hit the edges of the corresponding recesses 12 in the area of the fastening area B. As a result, the resiliently designed snap-in tongues 11 spring in in the radial direction. The chamfers 11.2 facilitate insertion. Upon reaching the connection position according to 17 the locking tongues 11 spring out transversely to the lancing 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 delivery 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 latching tongues 11, a relative rotation of the drive unit 3 with respect to the conveyor unit 2 blocked. No additional tools are required to produce the snap hook connection 60

In the connection position, the correspondingly designed guide elements 19, 20 of the intermediate element 6 and the fastening area B also engage in one another. This enables additional protection against relative rotation of the conveyor unit 2 with respect to the drive unit 3.

The tip of the latching tongue 11 can have a suitable colored marking which is visible from the outside in the latched connection position and is designed as a connection indicator 36 . In particular, a marking can be arranged in an area between the insertion bevel 11.2 and the latching area 11.1. It can thus be recognized in a simple manner whether the snap hook connection 60 has been produced correctly. If the latching tongues 11 do not latch completely with the recesses 12, an edge of the recess 12 covers the colored marking, which means that the assembly personnel can identify an assembly error.

The depictions in the Figures 21 to 23 show different pump arrangements 100, which are described below.

The pump assemblies 100 each have a delivery unit 2 , a drive unit 3 connected thereto and one or more valve units 18 .

The delivery unit 2 has at least two connecting elements 27 , 28 for the detachable connection of the delivery 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 in the exemplary embodiment shown and arranged laterally on the delivery 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 housing of the valve units 18 can move in the same direction (cf. 21 ) or in the opposite direction (cf. 22 ), or perpendicular to each other (cf. 23 ) extend.

Alternatively, the connecting elements for connecting the delivery unit 2 to the valve unit 18 can also be designed as latching tongues and corresponding recesses for producing a snap hook connection.

The bayonet connection 70 and the snap hook connection can be designed in accordance with the latching connections between the conveyor unit 2 and the drive unit 3 described above.

The valve units 18 can also be connected to one another by means of corresponding connecting elements 29, 30, cf. 23 . In this way, series arrangements of valves can 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 be designed in particular 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 the tool-free, detachable connection of the conveyor unit 2 and the drive unit 3 is described below.

First, a method for connecting the conveyor unit 2 and the drive unit 3 via a bayonet connection 50 according to the first embodiment will be described.

For connection, the drive unit 3 is moved axially aligned in the insertion direction R along the drive axis A toward the delivery unit 2 , with the intermediate shaft 14 engaging in a corresponding round bore of the fastening area B. Furthermore, the bayonet hooks 7 engage in the plug-in areas 8.1 of the respective recesses 8, cf. 9c . As soon as the intermediate element 6 and the conveyor unit 2 lie flat against one another, the drive unit 3 and thus the intermediate element 6 are rotated clockwise relative to the conveyor unit 2 . The latching parts 7.2 of the bayonet hooks 7 latch with the securing areas 8.2 of the respective recesses. Furthermore, when the connection position is reached, the safety lug 10.2 of a reverse rotation safety device 10 snaps into a corresponding safety recess 10.3 of the intermediate element 6, cf. Fig. 9e . In addition, tolerances are compensated for when the conveyor unit 2 and the drive unit 3 rotate relative to one another by the compensation ramps 9, which can deform to compensate for tolerances, cf. Figure 12b .

When connecting the delivery unit 2 to the drive unit 3, the actuating contour 14.1 of the intermediate shaft 14 engages with the corresponding actuating contour 16.1 of the driven gear wheel 4.1.

Such a bayonet connection 50 between delivery unit 2 and drive unit 3 is released using the same steps described above in reverse order. Furthermore, the turning and plugging directions are reversed accordingly.

Finally, a method for connecting the conveyor unit 2 and the drive unit 3 via a snap hook connection 60 according to the second embodiment is described.

For connection, the drive unit 3 is moved in the plug-in direction R along the drive axis A towards the delivery unit 2 , with the intermediate shaft 14 engaging in a corresponding round bore of the fastening area B. Furthermore, the locking tongues 12 engage with their tips in the recesses 11, cf. 17 . With further insertion, the insertion bevels 11.2 of the latching tongues 11 come into contact with the edges of the recesses 12, as a result of which the latching tongues 11 deflect radially inwards with further axial displacement. When the connection position is reached, the latching tongues 11 spring out automatically and the latching area 11.2 of the latching tongues 11 latches with the latching area 12.1 of the respective recess 12, cf. 20 .

When connecting the delivery unit 2 to the drive unit 3, the actuating contour 14.1 of the intermediate shaft 14 engages with the corresponding actuating contour 16.1 of the driven gear.

Such a snap hook connection 60 between conveyor unit 2 and drive unit 3 is released by applying a releasing force counter to the insertion direction R. This allows the latching areas 11.2 of the latching tongues 11 to disengage from the latching areas 12.1 of the recesses 12 and the connection to be released.

The gear pump 1 described above, the pump assembly 100 and the method for connecting the delivery unit 2 and the drive unit 3 of a gear pump 1 are characterized by a simple and fault-prone connection of the drive unit 3 with the conveyor unit 2, which can also be carried out safely by inexperienced assembly personnel.

References:

1

gear pump

2

conveyor unit

2.1

Housing

2.2

Lid

2.3

Wall

3

drive unit

3.1

Connection

3.2

drive shaft

4.1

gear

4.2

gear

5

connection area

6

intermediate element

7

fastener; bayonet hook

7.1

base

7.2

locking part

8th

fastener; recess

8.1

mating area

8.2

security area

9

balancing ramp

10

anti-reverse device

10.1

safety hook

10.2

safety nose

10.3

securing recess

11

fastener; locking tongue

11.1

rest area

11.2

lead-in bevel

12

fastener; recess

12.1

rest area

13

shaft bearing

14

intermediate shaft

14.1

actuating contour

14.2

shaft connection

15

shaft seal

16.1

actuating contour

16.2

bearing contour

17

bearings

18

valve unit

19

guide element

20

guide element

21

axis

22

fasteners; connector element

23

fasteners

24

mounting hole

25

poetry

26

Connection

27

fastener; bayonet hook

28

fastener; recess

29

fastener

30

fastener

31

enema

32

outlet

33

recess

34

annulus segment

35

gear room

36

connection indicator

37

intermediate element

50

bayonet connection

60

snap hook connection

70

bayonet connection

100

pump assembly

A

drive axle

B

mounting area

D

axis of rotation

R

mating direction

Claims (15)

Gear pump for delivering a fluid with a delivery unit (2) having at least two gears (4.1, 4.2) and a drive unit (3) driving the gears (4.1, 4.2), which can be released via connecting elements (7, 8, 11, 12) that can be operated without tools are connected
characterized,
that the connecting elements (7, 8, 11, 12) are designed as latching elements. Gear pump according to Claim 1, characterized in that connecting elements (7, 12) are arranged on the delivery unit (2) and connecting elements (8, 11) on the drive unit (3) and are designed to correspond to one another. Gear pump according to Claim 1 or 2, characterized in that the connecting elements (7, 8) form a bayonet connection (50). Gear pump according to Claim 3, characterized in that the connecting elements (7, 8) are designed as bayonet hooks and/or corresponding recesses. Gear pump according to Claim 4, characterized in that the bayonet hooks (7) have an essentially rectangular shape with a base (7.1) and a latching part (7.2) which spreads out at right angles from the base. Gear pump according to Claim 4 or 5, characterized in that the recesses (8) have an insertion area (8.1) for insertion the bayonet hook (7) and a safety area (8.2) for latching the bayonet hook (7). Gear pump according to Claim 6, characterized in that the securing areas (8.2) have a compensating ramp (9) for tolerance compensation, which is designed to interact with the latching parts (7.2) of the respective bayonet hooks (7). Gear pump according to one of Claims 3 to 7, characterized in that the bayonet connection (50) has a reverse rotation safety device (10). Gear pump according to one of Claims 1 or 2, characterized in that the connecting elements (11, 12) form a snap hook connection (60). Gear pump according to Claim 9, characterized in that the connecting elements (11, 12) are designed as resilient latching tongues and/or corresponding recesses. Gear pump according to one of the preceding claims, characterized in that the connecting elements (7, 8, 11, 12) are formed on at least one intermediate element (6), the intermediate element (6) on the delivery unit (2) and/or the drive unit ( 3) is fixed. Gear pump according to one of the preceding claims, characterized in that the drive unit (3) for driving the gears (4.1, 4.2) is operatively connected to the gears (4.1, 4.2) via an intermediate shaft (14). Gear pump according to one of the preceding claims, characterized by a connection indicator (36) showing the connection between the delivery unit (2) and the drive unit (3). Pump arrangement with a gear pump (1) and at least one valve unit (18),
characterized,
that the gear pump (1) is designed according to one of the preceding claims. Method for detachably connecting a delivery unit (2) and a drive unit (3) of a gear pump (1) via connecting elements (7, 8, 11, 12) that can be operated without tools.
characterized,
that the connecting elements (7, 8, 11, 12) are locked together.

Images