Patent Grant
11953007
The present application claims the benefit under 35 U.S.C. §§ 119(b), 119(e), 120, and/or 365(c) of PCT/EP2019/085094 filed Dec. 13, 2019, which claims priority to German Application No. 20 2018 107 141.6 filed Dec. 13, 2018.
The invention relates to a rotary lobe pump for conveying a particle-laden conveyed medium, comprising a pump housing with a pump room, an inlet opening and an outlet opening, a first multi-lobe rotary piston, which is arranged in the pump room and is rotatably mounted about a first axis of rotation, a second multi-lobe rotary piston, which is arranged in the pump room and is rotatably mounted about a second axis of rotation spaced apart from the first axis of rotation and meshingly engages in the first rotary piston, wherein the first and second rotary pistons are drivable in opposite directions and are designed to generate a flow of the conveyed medium from the inlet opening through the pump room to the outlet opening by counter-rotation about the first and second axis of rotation, respectively, and a drive device, which is mechanically coupled to the rotary pistons for driving the rotary pistons. The invention further relates to a sleeve for a rotary lobe pump. The invention also relates to a method for servicing a rotary lobe pump.
Rotary lobe pumps of the aforementioned design are used to pump liquids, in particular, particle-laden liquids. Liquids with varying or fluctuating solid contents can be pumped. Rotary lobe pumps are characterised in that they can reliably fulfil their function even with higher solid contents. In addition, rotary lobe pumps of this type are suitable for pumping both low and high viscosity liquids. Such pumps are typically used in agricultural technology or sewage technology, among others. Rotary lobe pumps are known, for example, from DE2002518A1, DE3427282A1, DE29723984U1, EP1519044B1, DE202010011626U1, EP2475889B1, WO2014/067988A2 and U.S. Pat. No. 2,848,952.
Rotary lobe pumps of the type according to the invention have a ball passage of at least 1 cm, preferably at least 2 cm, 5 cm, or even at least 7.5 cm. This means that spherical solid particles with a diameter of up to a maximum of 1 cm, 2 cm, 5 cm, or 7.5 cm can be conveyed through the pump room from the inlet to the outlet opening without jamming the moving components of the rotary lobe pump.
A fundamental problem that arises with such rotary lobe pumps is due to the fact that the replacement of wearing parts is associated with a relatively high effort, which has a negative effect on the maintenance costs and can also lead to longer downtimes of the rotary lobe pumps. From EP1519044B1 a rotary lobe pump is known which is accessible from one side, whereby the accessibility of the wearing parts is improved compared to conventional rotary lobe pumps. However, with this design, the executable length of the rotary piston is severely limited, since the drive shaft, which is connected to the rotary piston, is only mounted on one side of the rotary piston and therefore cannot be of any length.
From DE202010015437U1 a rotary lobe pump with hollow rotary piston is known. This offers the advantage that the rotary pistons can be more easily removed from and reinserted into the pump room, because the hollow rotary pistons can be guided axially onto the connection to the drive shaft. In particular, these rotary pistons can be inserted into the pump housing one after the other, as the drive shafts can be designed shorter than the rotary pistons. However, a disadvantage of such a rotary lobe pump is that wearing parts, such as the bearings and seals, cannot be replaced as easily as the rotary pistons.
Another general problem is that such pumps have a relatively high weight and are relatively large due to their design, which is negative in particular for the mobile use of such pumps, for example when used in or on vehicles.
It is, therefore, the task of the invention to provide a rotary lobe pump for conveying a particle-laden conveyed medium, which reduces or eliminates one or more of the disadvantages mentioned. In particular, it is the task of the invention to provide a solution in which the design of the rotary lobe pump is maintenance-friendly without reducing the load capacity of the pump.
According to the invention, this task is solved by a rotary lobe pump with the features of claim 1. The rotary lobe pump described at the beginning is characterised by a first fixed axle body, which is connected to the pump housing and which is arranged inside the first rotary piston, and at least one first bearing for rotatably bearing the first rotary piston about the first fixed axle body, wherein the bearing is arranged on an outer surface of the first fixed axle body and inside the first rotary piston.
The pump room is understood to be the pump room in which the rotary pistons are located and through which the conveyed medium is conveyed. The conveyed medium flows preferably via a pipe through the inlet opening into the pump room. There, the conveyed medium is conveyed towards the outlet opening by rotating the rotary pistons. The conveyed medium then flows through the outlet opening, preferably into a pipe connected to the outlet opening. Thereby, the rotary pistons are mounted to rotate about an axis of rotation. The first axis of rotation is defined as a virtual line running along the axis of rotation of the first rotary piston. The second axis of rotation is defined as a virtual line running along the axis of rotation of the second rotary piston. The multi-lobe rotary pistons preferably comprise at least two piston lobes, wherein by lobes or piston lobes is meant the displacement lobes of the rotary pistons. The lobes of the rotary pistons are in meshing engagement with each other. A drive device is mechanically coupled with the rotary pistons and drives the rotary pistons. For example, both rotary pistons can be driven individually by means of two electric motors or by means of two hydraulic motors. Alternatively, only one rotary piston can be driven by the drive device and the second rotary piston is driven by the meshing engagement with the first rotary piston. In this way, both rotary pistons can be driven directly, thereby providing each rotary piston with its required power directly, or one rotary piston can be driven directly and the other rotary piston indirectly via this rotary piston. The drive device can preferably comprise an electric or a hydraulic motor. The drive device can also be formed by a drive flange which can be coupled to a shaft output, for example, in order to drive the pump via a power take-off of a tractor or other vehicle. It is further possible that, for example, a drive device drives two shafts via a gearbox, wherein one shaft is coupled to the first rotary piston and another shaft is coupled to the second rotary piston. With all the drive options mentioned, synchronisation of the rotary pistons can be achieved.
The fixed axle body refers to a preferably rotationally symmetrical element that is connected to the pump housing. Thereby, the connection to the pump housing can be carried out by form closure, material closure, or force closure, for example, by means of a screw connection, or a combination thereof. The material closure fastening allows for a secure centring of the axle body on the pump housing and an exact axial alignment, which can be realised with the concept according to the invention, because the axle body, contrary to known solutions, does not have to be dismountable. The force closure also achieves—with increased manufacturing effort—such a good and fault-tolerant centring and additionally provides the option of replacing the axle body. The first fixed axle body extends along the first axis of rotation inside the first rotary piston. Thereby, preferably at least one bearing is arranged on the first fixed axle body. The bearing enables a rotatable mounting of the rotary piston about the first fixed axle body. The bearing is arranged inside the first rotary piston, in particular between the first end face and the second end face of the rotary piston.
The present invention offers the advantage that a very compact design can be achieved due to the location of the bearing inside the rotary pistons. Since there is no need for a bearing in or next to the pump housing, installation space is saved. Furthermore, the drive shaft does not have to be supported, as the bearing can be placed on the fixed axle body directly in the rotary pistons. Thereby, the pump is not limited in its load capacity compared to conventional rotary lobe pumps. This means that lighter and more compact rotary lobe pumps can be manufactured, which is in particular advantageous for mobile applications.
Furthermore, the invention has the advantage that larger chamber lengths can be realised than is the case with rotary lobe pumps with conventional bearing positions. Due to the internal bearing, any and optimal bearing points can be realised, as the position of the bearing is not limited to the ends of the rotatable parts.
According to a first preferred embodiment, it is provided that the first fixed axle body extends along the first axis of rotation, the first rotary piston extends from a first end face of the piston in axial direction to a second end along the first axis of rotation, and the first bearing is arranged axially with respect to the first axis of rotation between the first and second end face of the piston.
The fixed axle body can be designed in different lengths. For example, the axle body can be designed as a hollow cylinder or as a cylinder made of solid material. In the case of the design as a hollow cylinder, preferably a drive shaft can run through the fixed axle body. Preferably, the virtual axis of rotation of the fixed axle body runs on the first axis of rotation. Axial with respect to the first axis of rotation means along or in the direction of the virtual line defining the axis of rotation. The first bearing is preferably arranged inside the first rotary piston. The bearing is therefore preferably arranged between the two end faces of the first rotary piston.
According to a further preferred embodiment, the first bearing is designed as a rolling bearing. In this embodiment, a rolling bearing is used as first bearing to support the first rotary piston rotatably about the first axis of rotation.
A further preferred embodiment is characterised in that a second bearing, preferably designed as rolling bearing, is provided for rotatably supporting the first rotary piston about the first axis of rotation, wherein the second bearing is arranged on the outer surface of the first fixed axle body and inside the first rotary piston. Thereby, the second bearing is arranged on the fixed axle body and rotatably supports the first rotary piston about the first axis of rotation.
Another preferred embodiment is characterised by a second fixed axle body connected to the pump housing and arranged inside the second rotary piston, and at least one bearing for rotatably supporting the second rotary piston about the second axis of rotation, wherein the second bearing is arranged on the outer surface of the second fixed axle body and inside the second rotary piston.
In this embodiment, the two fixed axle bodies are arranged in such a way that the first fixed axle body extends at least partially inside the first rotary piston and the second fixed axle body extends at least partially inside the second rotary piston.
It is further preferred that the first drive device comprises a first drive unit and a second drive unit and that the first rotary piston is directly coupled to the first drive unit and the second rotary piston is directly coupled to the second drive unit. In this context, direct coupling of the drive units to the rotary pistons means that substantially no torque is transferred from the first rotary piston to the second rotary piston or from the second rotary piston to the first rotary piston. The drive units may be, for example, electric motors or hydraulic motors. The drive devices can be synchronised so that the rotary pistons are driven equally. The drive devices can both be arranged on one side of the pump housing. This offers a maintenance advantage. In this way, access to the components located inside the pump room and access to the pump room can be easily managed. The terms pump room and pump chamber can be used interchangeably. For example, an opening in the pump housing that can be closed with a lid can be opened to access the pump room and/or the components in the pump room. This offers significant advantages in terms of maintenance of the rotary lobe pump. Alternatively, the drive devices can be arranged on opposite sides of the pump housing. This type of arrangement offers the advantage that larger drives can be used, as more space is available for each drive device.
Still further, it is preferred that the first and the second rotary piston each have a number of N lobes, wherein N is greater than or equal to two, and the lobes of the first and second rotary piston extend helically along the circumferential surface of the rotary piston and thereby sweep an angle of at least 180° divided by N, preferably 240° divided by N, further preferably 300° divided by N, and preferably 360° divided by N.
This twisted geometry of the lobes of the rotary pistons offers the advantage that the rotary lobe pump can be operated without pulsation. Among other things, this reduces the load on the rotary lobe pump and the components of the rotary lobe pump.
It is further preferred that the first and the second rotary piston each have a number of N lobes, wherein N is preferably less than or equal to eight, less than or equal to six, or less than or equal to four. The number of lobes is, therefore, a maximum of eight in this preferred embodiment.
A further embodiment is characterised by a first seal for sealing from the first and/or the second bearing to the pump room, arranged between the first fixed axle body and the first rotary piston inside the rotary piston, wherein the first seal is preferably designed as a dynamic seal, in particular, as a sliding seal, particularly preferably as an axial or radial seal, for example, as an axial face seal or as a rotary shaft seal.
The bearings that rotatably support the first rotary piston are preferably sealed against the space inside the pump housing by means of a dynamic seal.
It is further preferred that the first seal for sealing from the first and/or the second bearing to the pump room is arranged at a first end of the bearings and is designed as a dynamic seal, in particular, as a sliding seal, particularly preferably as a rotary shaft seal, and a second seal for sealing from the first and/or the second bearing to the pump room is arranged at a second end of the bearings and is designed as a static seal, particularly preferably as an O-ring.
It is particularly advantageous that a dynamic seal only has to be used on one side of the bearing and a static bearing can be used on the other side of the bearing. This offers the advantage that the static seal can be much more robust and durable than a dynamic seal. Thus, an additional advantage is that wearing parts need to be replaced less frequently.
Still further preferred is that the first and/or the second bearing and the first seal are arranged inside a sleeve, wherein the sleeve is connected to the first and/or the second bearing, the sleeve inside the first rotary piston is detachably, preferably by force closure, connected to the rotary piston to rotate with the rotary piston.
The sleeve is preferably connected to the first and/or second bearing and to the first seal. The first and/or second bearing and the first seal are preferably arranged between the first end and the second end of the sleeve. The sleeve can be connected to the rotary piston. This is possible, for example, in such a way that the sleeve or a part of the sleeve can be spread. Preferably, a connection by force closure between the sleeve and the first rotary piston can then be established by spreading the sleeve.
A further preferred embodiment is characterised by a clamping device which is connected to the sleeve and is adjustable between an operating state and a release state, preferably by means of at least one screw connection, wherein in the operating preferably a force closure connection between the sleeve and the first rotary piston is present and in the release state the sleeve and the first rotary piston are movable relative to one another.
The clamping device can, for example, be designed integral with the sleeve or be detachably connected to the sleeve. In particular, the clamping device can also be non-detachably connected to the sleeve. Preferably, the clamping device is adjustable by means of at least one screw, so that a connection between the sleeve and the first rotary piston can be established. The connection between the sleeve and the rotary piston can, for example, be force closure and/or form closure. In the operating state, there is a connection between the sleeve and the first rotary piston. On the other hand, in the release state, relative movements between the sleeve and the rotary piston are possible.
It is further preferred if the clamping device has a tool engagement for relatively moving the clamping device and the sleeve in respect to the rotary piston. The tool engagement allows the clamping device to be connected to a tool, so that by means of a tool, which is connected to the clamping device, preferably via the tool engagement, the clamping device can be moved relatively along the axis of rotation.
In a further embodiment, it is preferred that the clamping device and the sleeve rest against a shoulder of the rotary piston inside the rotary piston and are releasably clamped against the shoulder, wherein the distance between the sleeve and the shoulder is adjustable, preferably by means of at least one screw connection of the clamping device, particularly preferably designed as at least one grub screw. Such a shoulder within the bore of the rotary piston enables a defined positioning of the components, which are arranged within the rotary piston. Thus, by means of a shoulder, precisely defined positions of the bearings and/or the sleeve and/or the seal or seals can be achieved.
It is further preferred that a washer is arranged between the sleeve and the shoulder of the rotary piston for adjusting the axial position of the first rotary piston relative to the sleeve. By means of a washer it is possible to adjust a defined position of the rotary piston in relation to the first fixed axle body and thus in relation to the pump room. Preferably, it is also possible to exchange this sleeve in order to adjust the position of the rotary piston in relation to the pump room.
A further preferred embodiment is characterised by a third fixed axle body connected to the pump housing and arranged inside the first rotary piston, and at least one bearing for rotatably supporting the first rotary piston about the first axis of rotation, wherein the bearing is arranged on the outer surface of the third fixed axle body and inside the first rotary piston.
In this embodiment, the first rotary piston is mounted around two fixed axle bodies. Thereby, the fixed axle bodies can, for example, both be designed as hollow cylinders, or one as a hollow cylinder and one made of solid material. With two axle bodies per rotary piston, even greater lengths of the rotary pistons can be realised, since also with long rotary pistons a sufficiently small bearing distance can be produced.
A further preferred embodiment is characterised by a fourth fixed axle body connected to the pump housing and arranged inside the second rotary piston, and at least one bearing for rotatably supporting the second rotary piston about the second axis of rotation, wherein the bearing is arranged on the outer surface of the fourth fixed axle body and inside the second rotary piston.
Even further is preferred that a hydraulic motor, preferably designed as a radial piston motor or toothed ring motor, is arranged inside the first rotary piston to drive the rotary piston.
In this embodiment, the hydraulic motor that drives the first rotary piston is arranged inside the pump housing. In particular, the hydraulic motor is arranged at least for the most part inside the first rotary piston. This design allows the rotary lobe pump to be made even more compact.
Further it is preferred that the hydraulic motor comprises a rotor rotatable about the first axis of rotation and mechanically coupled to the rotary piston inside the first rotary piston for driving the rotary piston, the hydraulic motor has a stator, which is arranged inside the rotor and connected to or integrally designed with the first fixed axle body, and an inlet and an outlet are connected to the hydraulic motor and extend inside the first fixed axle body and preferably to outside the pump housing.
The rotor of the hydraulic motor is thereby preferably arranged outside the stator. The stator is preferably arranged inside the rotor. Furthermore, the rotor is preferably connected to the first rotary piston by means of a shaft-hub connection.
A further preferred embodiment is characterised in that the drive device for driving the rotary pistons drives two drive shafts coupled via a synchronisation gear, wherein a first drive shaft is mechanically coupled to the first rotary piston and a second drive shaft is mechanically coupled to the second rotary piston, and the synchronisation gear preferably has a spur gear or a toothed belt, in particular, a double toothed belt, for synchronously driving the drive shafts. In this embodiment, two drive shafts are driven via a gearbox, wherein preferably one of the drive shafts drives one of the rotary pistons in each case. The drive shafts are connected to the rotary pistons, for example, via a shaft-hub connection, in order to transmit a torque to them. The synchronisation gear is preferably designed in such a way that it drives the two drive shafts so that they rotate in opposite direction at the same rotational speed.
Further an embodiment is characterised by a shaft-hub connection, for transmitting a torque, which connects the first drive shaft and the first rotary piston in a torque-proof manner and is arranged inside the first rotary piston, wherein preferably the shaft-hub connection is connected to an internal thread inside the rotary piston. Thereby, particularly preferably, an internal thread is arranged within the first rotary piston, into which a screw is screwed, which is connected to the first drive shaft in order to transmit a torque from the drive shaft to the first rotary piston. Thereby, preferably, a clamping sleeve for transmitting a torque from the first drive shaft to the first rotary piston is connected to the screw.
Even further it is preferred that a second drive device is mechanically coupled to the second rotary piston for driving the second rotary piston. Thereby, the drive device is preferably connected to the rotary piston by means of a shaft-hub connection in order to transmit a torque from the second drive device, preferably via a drive shaft, to the second rotary piston.
Even further it is preferred that the first drive device and the second drive device are arranged on opposite sides of the pump housing. This type of arrangement offers the advantage that larger drives can be used, as more space is available for each drive device.
According to a further aspect of the present invention, the above-mentioned problem is solved by a servicing method comprising: Releasing a detachable, preferably force closure connection between a sleeve and a rotary piston, which are rotatably arranged in a pump room, wherein the sleeve is arranged inside the rotary piston, and axially pulling the sleeve out of the rotary piston, wherein at least one bearing and one seal are connected to the sleeve in such a way that they are moved axially out of the rotary piston with the sleeve when the sleeve is pulled out.
Thereby, the connection between the sleeve and the rotary piston can preferably be made by force closure and/or by form closure, for example, by means of a spreadable part through which the connection can be made and which is preferably located on the sleeve. Axially pulling of the sleeve from the rotary piston means that the sleeve is guided out of the rotary piston in the direction of the virtual axis of rotation of the rotary piston. For further advantages, embodiment variants and embodiment details of these further aspects and their possible further embodiments, reference is also made to the previously given description regarding the corresponding features and further embodiments of the rotary lobe pump.
Preferred embodiments of the invention are explained by way of example with reference to the accompanying figures. They show:
In the figures, identical or essentially functionally identical or similar elements are designated with the same reference signs.
| Number | Date | Country | Kind |
|---|---|---|---|
| 20 2018 107 141.6 | Dec 2018 | DE | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2019/085094 | 12/13/2019 | WO |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO2020/120746 | 6/18/2020 | WO | A |
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