EP3430263B1 - Diaphragm pump - Google Patents

Description

The invention relates to a diaphragm pump with the features specified in the preamble of claim 1.

Conventional diaphragm pumps have a pump housing approximately in the form of a carrier part and a drive motor held thereon with a drive shaft rotating about a main axis of rotation. A pump element in the form of a membrane is arranged in a pump head, which delimits a pump chamber and is driven in a swinging manner by the drive shaft of the motor via a suitable eccentric drive.

An inlet connection and an outlet connection are provided on the carrier part, each of which can be mutually connected to the pump chamber via a shuttle valve arrangement in the sense of an intake and exhaust stroke.

In conventional diaphragm pumps, this shuttle valve arrangement is formed by two passive check valves in corresponding inlet and outlet channels from and to the pump chamber, which show a certain disadvantageous dependence on changing ambient conditions. A positive pressure difference between inlet and outlet can also lead to an uncontrolled flow of pump medium through the pump.

In addition, the check valves mentioned are generally designed as diaphragm valves, which are not very well defined in terms of their opening and closing behavior, in particular for metering pumps, and are susceptible to wear.

Accordingly, known diaphragm pumps of this type are only of limited suitability, in particular for high-precision metering pumps.

Basically, in the case of metering pumps, as a replacement for the diaphragm valves recognized as disadvantageous, valve constructions with a valve disk are known, which can alternately be connected to corresponding kidney-shaped discharge channels with a flow opening. Such butterfly valve designs are for example from the DE 10 2012 200 501 A1 , the DE 31 22 722 A1 or the DE 34 16 983 A1 known. The problem with these constructions is the difficult control of the valve disc, which is the case, for example, with the construction DE 10 2012 200 501 A1 done by a magnetically coupled actuator disk.

The invention is accordingly based on the object of improving a diaphragm pump of the type described at the outset in such a way that the pumping behavior becomes more defined and precise and is more independent of external influences.

• der Pumpenkopf im Trägerteil rotierend gelagert und mit der Antriebswelle in einer Orientierung verbunden ist, dass die Schwingungsrichtung der Membran orthogonal zur Hauptrotationsachse der Antriebswelle gerichtet ist,
• für die Membran ein Antriebsübertragungselement vorgesehen ist, das
  • = einerseits auf dem Pumpenkopf in der Schwingungsrichtung der Membran verschiebbar gelagert und mit einem Koppelelement mit der Membran antriebskinematisch verbunden ist, sowie
  • = in einer exzentrisch zur Hauptrotationsachse drehbar gelagerten Lagerscheibe orthogonal zur Schwingungsrichtung der Membran verschiebbar geführt ist, derart, dass
  • = bei der von der Antriebswelle hervorgerufene Drehung der Pumpenkammer und der rotatorischen Mitnahme des Antriebsübertragungselementes durch die Pumpenkammer aufgrund der exzentritätsbedingten Verschiebungen des Antriebsübertragungselementes relativ zur Pumpenkammer und zur Lagerscheibe das Antriebsübertragungselement mit seinem Koppelelement die oszillatorische Bewegung der Membran in der Pumpenkammer erzeugt, sowie
• durch die Rotation des Pumpenkopfes eine darin angeordnete Pumpmediumleitung wechselweise mit dem Einlass- oder Auslassanschluss verbunden ist.

This object is achieved by the features specified in the characterizing part of claim 1. Accordingly, the diaphragm pump is characterized in that

• the pump head is rotatably mounted in the carrier part and is connected to the drive shaft in an orientation that the direction of vibration the diaphragm is oriented orthogonal to the main axis of rotation of the drive shaft,
• a drive transmission element is provided for the membrane, the
  • = on the one hand slidably mounted on the pump head in the direction of vibration of the diaphragm and connected to the diaphragm by a coupling element with the drive kinematics, and
  • = is guided in a bearing disc rotatably mounted eccentrically to the main axis of rotation and can be displaced orthogonally to the direction of vibration of the membrane, such that
  • = in the case of the rotation of the pump chamber caused by the drive shaft and the rotational entrainment of the drive transmission element by the pump chamber due to the eccentricity-related displacements of the drive transmission element relative to the pump chamber and to the bearing disk, the drive transmission element with its coupling element generates the oscillatory movement of the membrane in the pump chamber, and
• due to the rotation of the pump head, a pump medium line arranged therein is alternately connected to the inlet or outlet connection.

The combination of the features specified in the characterizing part of claim 1 achieves a valve control which is completely different from the prior art. In practice, the rotation of the shuttle valve arrangement is generated by the rotating mounting of the pump head, with this rotational movement simultaneously driving the membrane via the eccentrically arranged in a bearing disk and relative thereto and the pump head displaceable drive transmission element is derived. In summary, this results in a defined pump behavior that is practically independent of the external conditions at the inlet and outlet connection. The valve arrangement itself is low-wear because there is no need for diaphragm valves.

Preferred developments of the subject matter of the invention are specified in the dependent claims. Thus, the drive transmission element can be designed as a cage-like part, which is guided with sliding guides relative to the pump head on the one hand and the bearing plate on the other hand. This represents a structurally simple design for this component, with which the circumferential relative displacement of the drive transmission element caused by the eccentricity of the bearing of the drive transmission element relative to the pump head is made possible without problems.

The coupling element of the drive transmission element can be designed as a coupling pin projecting inward into the pump head, which is connected to the membrane and thus transmits the movement of the drive transmission element during rotation to the membrane in the sense of an oscillatory movement.

According to a further preferred embodiment, the bearing disk can be rotatably mounted in a roller bearing ring on the carrier part. This represents a particularly exact and easy-running bearing of the bearing disc, which has proven to be particularly advantageous in connection with the application of the diaphragm pump according to the invention as a metering pump in the sense of an exact rotation.

Dimensions of up to 1/3, preferably up to 1/5, of the diaphragm clamping diameter can be specified for the eccentricity of the bearing disc's bearing with respect to the main axis of rotation, with about 1/10 being the upper limit for flat diaphragms. The larger eccentricities then come into question for other types of membranes, such as beads or roller membranes.

In order to integrate the type of disk valve described at the outset into the diaphragm pump according to the invention, a preferred further development provides that the pumping medium channel leads from the pump chamber parallel to the main axis of rotation in the pump head to a two-kidney-shaped partial ring channels in the carrier part, via which the pumping medium channel alternately in the sense of a Intake and exhaust stroke is connectable to the inlet connection or outlet connection of the pump. The rotation of the pump chamber not only derives the drive of the membrane, but also the control of the shuttle valve arrangement.

Preferred developments of the shuttle valve arrangement provide for the equipment with a rotating sealing disk with a valve opening, via which the pump medium channel can be connected alternately to the inlet connection or outlet connection. In particular, if the shuttle valve arrangement is arranged on the carrier part under spring action in the direction of the sealing disk, the valve arrangement permanently has a high level of tightness. Furthermore, the sealing washer, with a correspondingly low-friction design, can achieve a wear-free, smooth running of the diaphragm pump.

Another preferred embodiment of the invention relates to the pump head, which can be composed of a lower part and an upper part with a membrane clamped in between. The coupling element of the drive transmission element, in particular the coupling pin, then projects through an opening in the lower part into the pump head for connection to the membrane.

If there was previously talk of a pump head with a pump chamber and correspondingly a pump element, then advantageous further developments can be realized in that two or more pump chambers are provided next to one another with pump elements running counter or offset with respect to their cycle. These can then be driven jointly by the drive transmission element via separate coupling elements. Multiple pumping chambers and diaphragms can be used to even out the delivery behavior of the diaphragm pump without sacrificing metering accuracy, for example in the case of a microdosing pump, since the individual pumping chambers operate with a clocked offset, so that if one pumping chamber is working, for example, in the intake stroke, the other pumping chamber is currently running in the discharge stroke.

• Es handelt sich um eine kompakte Membranpumpe mit gesteuerten Ventilen und einem geregelten Motor.
• Durch den speziellen Exzenterantrieb wird die Membran streng linear betätigt, was ein sehr steifes Design und eine PTFE-Beschichtung der Membran erlaubt.
• Die Ventilkonstruktion erfordert nur eine statische Abdichtung und keine sich biegenden Elastomeren. Dies führt zu Pumpen mit sehr hoher chemischer Widerstandsfähigkeit und einer langen Lebensdauer. Weiterhin zeigt die Pumpe keine Neigung zur Leckage gegenüber der Umwelt.
• Unabhängig vom Motorlauf oder jeglicher Anhalteposition des Motors besteht zu keiner Zeit ein offener Strömungsweg zwischen dem Einlass und Auslass der Pumpe in jedweder Richtung.
• Die Konstruktion der Pumpenkammer und der Ventile vermeidet Volumenbereiche ohne direkten Kontakt mit dem Flüssigkeitsstrom. Dementsprechend ist das Spülen und Reinigen des Pumpenkopfes einfach realisierbar.
• Eine steife Membran in Verbindung mit gesteuerten Ventilen führt zu optimierten Druck- und Saugeigenschaften für Gase, Flüssigkeiten und Mischungen von Gasen und Flüssigkeiten.
• In Verbindung mit einem geschwindigkeits- und richtungsgesteuerten Motor, wie er beispielsweise durch eine Schrittmotor realisiert werden kann, ist der Pumpstrom exakt einstellbar und kann ferner durch eine Richtungsumkehr der Motorrotation einfach reversiert werden. Aufgrund der geringen Elastizitäten im gesamten Aufbau ist die Strömungsrate zeitlich sehr konstant und Umwelteinflüsse werden minimiert. Die Strömung ist nahezu unabhängig von sich änderndem Rück- oder Einlassdruck und bleibt sogar dann konstant, wenn am Einlass der Pumpe ein Überdruck herrscht.
• Mit einer optionalen Positionserfassung können Fehlschritte, wie beispielsweise ausgelassene Schritte, des Schrittmotors kompensiert werden. Dies erlaubt ferner ein ganz bestimmtes, definiertes Volumen durch Zählung der Motorumdrehungen abzugeben.
• Insgesamt zeigt die erfindungsgemäße Pumpe eine hohe Strömungspräzision von beispielsweise 1 Prozent und darunter auf. Sie ist ruhig und arbeitet mit sehr geringen Vibrationen.
• Die reale Konstruktion der Membranpumpe für die Serienproduktion ist in hohem Maße an die jeweiligen Anforderungen der Anwendung anpassbar. So sind die Strömungsraten in Größenordnungen zwischen µl/min bis l/min skalierbar. Das Material der benetzten Bereiche kann der erforderlichen chemischen Widerstandsfähigkeit entsprechen. Die Flüssigkeitsanschlüsse sind oben am Kopf der Pumpe angeordnet, wobei deren Detailposition und -ausrichtung frei wählbar sind. Für die benetzten Teile der Pumpe kann eine hohe Wartungsfreundlichkeit, beispielsweise für einen leichten Austausch, erzielt werden. Durch das robuste Design der Pumpenteile können auch Medien mit hohen Viskositäten gefördert werden.

The advantages of the diaphragm pump according to the invention with its preferred designs can be summarized as follows:

• It is a compact diaphragm pump with controlled valves and a regulated motor.
• The membrane is actuated in a strictly linear manner by the special eccentric drive, which allows a very rigid design and a PTFE coating on the membrane.
• The valve construction only requires a static seal and no flexing elastomers. This leads to pumps with a lot high chemical resistance and a long service life. Furthermore, the pump shows no tendency to leak towards the environment.
• Regardless of the engine running or any stopping position of the engine, there is never an open flow path between the inlet and outlet of the pump in any direction.
• The design of the pump chamber and valves avoids volume areas without direct contact with the liquid flow. Accordingly, the rinsing and cleaning of the pump head is easy to implement.
• A rigid membrane in connection with controlled valves leads to optimized pressure and suction properties for gases, liquids and mixtures of gases and liquids.
• In connection with a speed- and direction-controlled motor, as can be realized for example with a stepper motor, the pump current can be set exactly and can also be easily reversed by reversing the direction of the motor rotation. Due to the low elasticity in the entire structure, the flow rate is very constant over time and environmental influences are minimized. The flow is almost independent of changing return or inlet pressure and remains constant even if there is overpressure at the pump inlet.
• With an optional position detection, incorrect steps, such as omitted steps, of the stepper motor can be compensated for. This also allows a very specific, defined volume to be delivered by counting the engine revolutions.
• Overall, the pump according to the invention shows a high flow precision of, for example, 1 percent and below. It is calm and works with very little vibration.
• The real design of the diaphragm pump for series production is highly adaptable to the respective requirements of the application. The flow rates are scalable in the order of magnitude between µl / min to l / min. The material of the wetted areas can correspond to the required chemical resistance. The liquid connections are arranged at the top of the pump head, the detail position and orientation of which can be freely selected. The wetted parts of the pump can be easily maintained, for example for easy replacement. Thanks to the robust design of the pump parts, media with high viscosities can also be pumped.

Fig. 1

eine perspektivische Darstellung einer Membranpumpe,

Fig. 2

einen ausschnittsweisen Axialschnitt der Pumpe gemäß Schnittlinie II-II nach Fig. 1,

Fig. 3

einen Radialschnitt durch die Pumpe gemäß Schnittlinie III-III nach Fig. 2,

Fig. 4

eine Seitenansicht einer schematisiert dargestellten Membranpumpe,

Fig. 5

eine Ansicht der Membranpumpe gemäß Pfeilrichtung V nach Fig. 4 in einer Neutralposition der Membran,

Fig. 6

einen Axialschnitt entlang der Schnittlinie VI-VI nach Fig. 5,

Fig. 7

einen Radialschnitt entlang der Schnittlinie VII-VII nach Fig. 4,

Fig. 8 bis 10

Darstellungen der Membranpumpe analog den Fig. 5 bis 7 in einer gegenüber der Neutralposition um 45° gedrehten Position des Pumpenkopfes mit Antriebskäfig,

Fig. 11 bis 13

Darstellungen der Membranpumpe analog den Fig. 5 bis 7 im oberen Totpunkt des Pumpenkopfes mit Antriebskäfig,

Fig. 14 bis 16

Darstellungen der Membranpumpe analog den Fig. 5 bis 7 im unteren Totpunkt des Pumpenkopfes mit Antriebskäfig,

Fig. 17

eine perspektivische Explosionsdarstellung der Wechselventilanordnung der Membranpumpe,

Fig. 18 und 19

Darstellungen analog den Fig. 6 und 7 einer Membranpumpe mit doppelter Pumpenkammer, und

Fig. 20

eine perspektivische Darstellung einer Wechselventilanordnung für die Membranpumpe gemäß Fig. 18 mit doppelter Pumpenkammer.

Further features, details and advantages of the invention will become apparent from the following description of an embodiment with reference to the accompanying drawings. Show it:

Fig. 1

a perspective view of a diaphragm pump,

Fig. 2

a partial axial section of the pump according to section line II-II Fig. 1 .

Fig. 3

a radial section through the pump according to section line III-III Fig. 2 .

Fig. 4

a side view of a diaphragm pump shown schematically,

Fig. 5

a view of the diaphragm pump according to the direction of arrow V. Fig. 4 in a neutral position of the membrane,

Fig. 6

an axial section along the section line VI-VI Fig. 5 .

Fig. 7

a radial section along the section line VII-VII Fig. 4 .

8 to 10

Representations of the diaphragm pump analog 5 to 7 in a position of the pump head with drive cage rotated by 45 ° compared to the neutral position,

11 to 13

Representations of the diaphragm pump analog 5 to 7 at the top dead center of the pump head with drive cage,

14 to 16

Representations of the diaphragm pump analog 5 to 7 at the bottom dead center of the pump head with drive cage,

Fig. 17

3 shows an exploded perspective view of the shuttle valve arrangement of the diaphragm pump,

18 and 19

Representations analogous to Fig. 6 and 7 a diaphragm pump with a double pump chamber, and

Fig. 20

a perspective view of a shuttle valve assembly for the diaphragm pump according to Fig. 18 with double pump chamber.

How from Fig. 1 and 2 becomes clear, the diaphragm pump shown has a frame-like support part 1, which acts as a pump housing and to which an electric drive motor 2 is attached. The one in the Fig. 4 ff. Only schematically indicated drive motor 2 has one about a main axis of rotation HR rotating drive shaft 3. A pump head, designated as a whole by 4, is composed of an upper part 5 and a lower part 6, which delimit a customary, lenticular work space. In this, a membrane 7 is clamped between the upper and lower parts 5, 6, which, together with the upper part 5, delimits the pump chamber 8. The pump head 4 is rotatably mounted in the carrier part 1 in a manner to be explained in more detail below and is connected to the drive shaft 3 in one orientation, so that the direction of vibration SR of the diaphragm 7 is oriented orthogonally to the main axis of rotation HR of the drive shaft 3.

How from Fig. 1 and 3 A bearing bridge 9 is provided on the carrier part 1 on the side facing away from the drive motor 2, from which connecting piece-like outlet connections 10 and inlet connections 11 protrude in the opposite direction. These connections 10, 11 are provided with a shuttle valve arrangement, designated as a whole by 12, which can be alternately connected to the pump chamber 8 in the sense of an intake and exhaust cycle. Their function is explained in more detail below.

To drive the membrane 7 in the pump head 4, a drive transmission element 13 is provided, which for the sake of simplicity is referred to below as the drive cage 13. On the one hand, this drive cage 13 is made of, for example Fig. 3 and 7 it becomes clear with lateral struts 14, 15 slidably mounted on the pump head 4 in the direction of vibration SR of the diaphragm 7 via slide guides 16. Furthermore, the drive cage 13 is seated in a bearing disk 17 which is rotatably mounted on the carrier part 1 in a roller bearing ring 18 serving as a rotary bearing. The drive cage 13 is in turn slidably supported in the bearing disk 17 in a direction which is oriented orthogonally to its guide direction on the pump head 4. For this purpose, the receptacle 20 Sliding guide 19 in the bearing washer 17 for the drive cage 13 is made wider than the corresponding dimension of the drive cage. In the same way, the opening in the drive cage 13 with the slide guides 16 for guiding on the pump head 4 is made wider than the corresponding dimension of the pump head 4. Thus, the drive cage 13 within the receptacle 20 and the pump head 4 can be relative to one another in the vibration direction SR of the membrane 7 and move orthogonally to it.

How from Fig. 3 , but particularly clear Fig. 9 . 12 and 15 can be seen, the bearing disk 17 with its rolling bearing ring 18 is arranged on the carrier part 1 such that the axis of rotation DA of the bearing disk 17 is arranged parallel to the main axis of rotation HR, but offset with an eccentricity EX.

Finally, it should be noted that the drive cage 13, as a coupling element with the membrane 7, has a coupling pin 21 projecting inwards into the pump head 4, at the end of which the membrane 7 is fastened in the center. The coupling pin 21 accesses the membrane 7 via an opening 28 in the lower part 6 of the pump head 4.

How from Fig. 2 . 6 . 9 . 12 and 15 becomes clear, a pump medium channel 22 extends from the pump chamber 8 on the side facing away from the coupling pin 21, which runs parallel to the main axis of rotation HR at a distance from it towards the shuttle valve arrangement 12 and opens into the valve opening 23 of a valve disk 24. The latter rotates together with the pump head 4, which is rotatably mounted on this side via an axle stub 25 in the carrier part 1.

The valve disc 24 with the valve opening 23 cooperates with the shuttle valve arrangement 12, in which - as from Fig. 3 and 17 it becomes clear - two kidney-shaped partial ring channels 26, 27, which are fluidly connected to the inlet connection 11 and outlet connection 10, are introduced on a circular line corresponding to the circumferential diameter of the valve opening 23.

The operation of the in the 1 to 17 The diaphragm pump shown is to be explained as follows:
In the 5 to 7 the diaphragm pump is shown in the neutral position of the diaphragm 7, ie the middle position between the bottom and top dead center. When the pump head 4 rotates due to the drive motor 2, the pump head 4 rotates and takes the drive cage 13 with it via the slide guides 16. Due to the eccentricity EX of its storage in the bearing disc 17 with respect to the main rotation HR, about which the pump head 4 rotates, the drive cage 13 moves during this rotation along the slide guides 16 and 19 relative to the pump head 4 and bearing disc 17, as a result of which the drive cage 13 with its Dome pin 21 engages deeper in the pump head 4 and accordingly moves the diaphragm 7 in the direction of top dead center. A 45 ° intermediate position during this movement is in the 8 to 10 shown.

Upon further rotation of the drive shaft 3 of the pump head 4, the drive cage is moved further relative to the pump head 4 until the membrane has reached top dead center, as shown in FIG 11 to 13 is shown. The pump head 4 has compared to that in the 5 to 7 shown neutral position rotated by 90 °. The corresponding movement of the diaphragm 7 corresponds to the discharge stroke of the diaphragm pump during which the pump medium channel 22 leads via the valve opening 23 to the one partial ring channel 27, which is connected to the outlet connection 10. The medium located in the pump chamber 8 is therefore expelled through the outlet connection 10. When the top dead center of the diaphragm 7 is reached, the rotation angle of the pump head 4 is also such that the pump medium channel 22 with the valve opening 23 in the valve disk 24 leaves the overlap with the partial ring channel 27, so that the pump medium channel 22 is sealed off at this moment.

When the drive shaft 3 with the pump head 4 rotates further through 180 °, the relative movement from the drive cage 13 to the pump head 4 is reversed and the neutral position is run through again until it reaches the position shown in FIG 14 to 16 Shown bottom dead center position of the drive cage 13 with the membrane 7 is reached. During this rotational movement, the pump medium channel 22 with the valve opening 23 in the valve disk 24 is in overlap with the second partial ring channel 26, so that during this suction cycle, pump medium can be sucked into the pump chamber 8 via the inlet connection 11. When bottom dead center is reached, the pump medium channel 22 with the valve opening 23 is again closed outside the overlap area with the partial ring channel 26 and the pump chamber 8 in the filled state.

The due to the eccentricity EX of the mounting of the drive cage 13 within the rotatable bearing disc 17, the entrainment of the drive cage 13 by the pump head 4 and the mutual displacement of these elements in the direction of vibration SR and orthogonally to the oscillating movement of the drive cage 13 is in a comparison Fig. 6 . 7 . 9 . 10 . 12 . 13 . 15 and 16 clearly visible, so the drive mechanism it's clear. The amplitude of this oscillation movement of the membrane 7 corresponds to twice the eccentricity EX.

For the sake of completeness, it should also be added that the component which realizes the shuttle valve arrangement 12 with the outlet and inlet connection 10, 11 is acted upon by a pressure spring arrangement 29 in the bearing bridge 9 in the direction of the valve disk 24 and the pump head 4, so that a tight abutment of these components and a correspondingly tight closure of the shuttle valve arrangement 12 is ensured regardless of the pressure conditions at the inlet and outlet of the pump.

Based on 18 to 20 An alternative diaphragm pump with a double pump head 4 'can be explained, which has two pump chambers 8, 8' lying next to each other parallel to the main axis of rotation HR, each with a diaphragm 7, 7 '. The latter are clamped between the upper part 5 ', which jointly opposes both membranes 7, 7', and the two lower parts 6, 6 '. The drive kinematics corresponds to the pump diaphragm described above, the drive cage 13 only having a second coupling pin 21 ′ in opposition to the first coupling pin 21, which drives the second diaphragm 7 ′. How from Fig. 18 becomes clear, the pump medium channels 22, 22 'of the two pump chambers 8, 8' are each arranged on the mutually facing sides of the pump chambers 8, 8 'and lead to a valve disk 24', in which two valve openings 23, 23 'are offset by 180 °. are provided - see Fig. 20 , At the in Fig. 18 and 19 deflection of the membranes 7, 7 'shown in the same spatial direction is in the Fig. 18 The pump chamber 8 shown below reaches the top dead center position, that is, the end of the exhaust stroke, while in the pump chamber 8 'shown above, the membrane 7' is in the lower one Dead center position, i.e. at the end of the intake stroke. In this position, the valve disc 24 'takes the in Fig. 20 shown position of the shuttle valve assembly 12 'in the transition region between the two partial ring channels 26, 27. When the pump head 4 'continues to rotate and the corresponding displacement of the drive cage 13' with further movement of the two membranes 7, 7 ', the two valve openings 23, 23' come into connection with the respective other connection, so that it can be seen during a complete revolution of the pump head 4 'on Inlet connection 11 with short interruptions during the transition of valve openings 23, 23 'from one partial ring channel 26 to the other partial ring channel 27, there are always suction conditions and pressure conditions prevail at outlet port 10.

In addition, the diaphragm pump is according to the 18 to 20 in structure and operation in accordance with the diaphragm pump according to 1 to 17 , so that a repeated description is unnecessary. Matching components are provided with identical reference symbols.

Claims (10)

1. A diaphragm pump, comprising

   - a carrier part (1),
   a drive motor (2) which is arranged thereon and which has a drive shaft (3) which rotates about a main axis of rotation (HR),

   - a pump head (4, 4') with at least one pump chamber (8, 8') which is delimited by a diaphragm (7, 7') driven in oscillation, and

   - an inlet port (11) and outlet port (10), which are arranged on the carrier part (1) and which are each able to be alternately connected via a shuttle valve arrangement (12, 12') to the at least one pump chamber (8, 8') in the sense of an intake stroke and exhaust stroke, characterized in that

   - the pump head (4, 4') is mounted rotatably in the carrier part (1) and is connected to the drive shaft (3) in an orientation such that the direction of oscillation (SR) of the diaphragm (7, 7') is directed orthogonally with respect to the main axis of rotation (HR) of the drive shaft (3),

   - there is provided for the diaphragm (7, 7') a drive transmission element (13, 13'), which

   = firstly is mounted on the pump head (4, 4') so as to be displaceable in the direction of oscillation (SR) of the diaphragm (7, 7') and is connected to the diaphragm (7, 7') in terms of drive kinematics by way of a coupling element (21, 21'), and

   = is guided in a bearing disk (17), which is mounted so as to be rotatable eccentrically with respect to the main axis of rotation (HR), so as to be displaceable orthogonally with respect to the direction of oscillation (SR) of the diaphragm (7, 7'), such that,

   = owing to the eccentricity-induced displacements of the drive transmission element (13, 13') relative to the pump head (4, 4') and to the bearing disk (17), the drive transmission element (13, 13') generates, by way of its coupling element (21, 21'), the oscillatory movement of the diaphragm (7, 7') in the pump chamber (8, 8') during the rotation of the pump head (4, 4'), brought about by the drive shaft (3), and the rotational driving along of the drive transmission element (13, 13') by the pump head (4, 4'), and,

   - as a result of the rotation of the pump head (4, 4'), a pump medium line (22) arranged therein is alternately connected to the outlet port (10) and the inlet port (11).
2. The diaphragm pump as claimed in claim 1, characterized in that the drive transmission element (13, 13') is formed as a cage-like part, which is guided by way of sliding guides (16, 19) so as to be displaceable in relation to the pump head (4, 4') and to the bearing disk (17).
3. The diaphragm pump as claimed in claim 1 or 2, characterized in that the coupling element of the drive transmission element (13, 13') is formed as a coupling pin (21, 21') which projects inwardly into the pump head (4, 4') and which is connected to the diaphragm (7, 7').
4. The diaphragm pump as claimed in one of the preceding claims, characterized in that the bearing disk (17) is mounted rotatably in a rolling bearing ring (18) on the carrier part (1).
5. The diaphragm pump as claimed in one of the preceding claims, characterized in that the eccentricity (EX) of the mounting of the bearing disk (17) in relation to the main axis of rotation (HR) is up to 1/3, preferably up to 1/5, of the diaphragm clamping diameter.
6. The diaphragm pump as claimed in one of the preceding claims, characterized in that the pump medium duct (22) leads, in a manner parallel to, and at a distance from, the main axis of rotation (HR) in the pump head (4, 4'), from the pump chamber (8, 8') to a shuttle valve arrangement (12, 12'), having two kidney-shaped part-ring ducts (26, 27), in the carrier part (1), via which the pump medium duct (22) is able to be alternately connected to the inlet port (11) and the outlet port (10) in the sense of an intake stroke and exhaust stroke.
7. The diaphragm pump as claimed in claim 6, characterized in that, on the part of the shuttle valve arrangement (12, 12'), at the pump head (4, 4'), a sealing valve disk (24, 24') which rotates with the latter is provided with a valve opening (23, 23') via which the pump medium duct (22) is able to be alternately connected to the inlet port (11) and the outlet port (10).
8. The diaphragm pump as claimed in claim 7, characterized in that the shuttle valve arrangement (12, 12') is arranged on the carrier part (1) under spring loading (28) in the direction of the valve disk (24, 24').
9. The diaphragm pump as claimed in one of the preceding claims, characterized in that the pump head (4, 4') is made up of a bottom part (6) and a top part (5, 5') together with the diaphragm (7, 7') clamped therebetween, wherein the coupling element (21, 21') projects into the pump head (4, 4') through an opening (28) in the bottom part (6) for the purpose of connection to the diaphragm (7, 7').
10. The diaphragm pump as claimed in one of the preceding claims, characterized in that, in the pump head (4'), there are arranged mutually adjacently at least two pump chambers (8, 8') with diaphragms (7, 7') which move with opposing strokes and which are jointly driven by the drive transmission element (13') via separate coupling elements (21, 21').

Images