Patent Application
20250012275
This application claims the benefit and priority of German Application No. DE 102023117788.5 filed Jul. 6, 2023 and German Application No. DE 102023122127.2 filed Aug. 18, 2023. The entire disclosure of the above applications are incorporated herein by reference.
The invention relates to a gerotor pump for conveying a fluid and a motor/pump unit which has the gerotor pump.
Conventional gerotor pumps, also known as “toothed ring pumps” or “Eaton pumps”, have a rotatable outer rotor and a rotatable inner rotor, wherein the inner rotor is arranged radially inside the outer rotor. Generally, the inner rotor is driven by a motor. In this instance, the inner rotor is in the form of a gear and the outer rotor is in the form of a toothed ring, wherein the inner rotor and the outer rotor have rotation axes which differ from each other. The outer rotor thereby runs eccentrically on an external tooth arrangement of the inner rotor. As a result of the changing volumes between the tooth gaps between the inner rotor and outer rotor, pressure regions are formed, also referred to as pump chambers, by means of which the fluid is conveyed.
“Fundamentals of Designing Hydraulic Gear Machines” by Jaroslaw Stryczek (ISBN: 978-83-01-21226-1) and “Axial clearance compensation in the gerotor pump” by Jaroslaw Stryczek and Slawomir Bednarczyk from “The 19th International Conference on Hydraulics and Pneumatics, Prague, Sep. 29-Oct. 1, 2008” describe conventional axial compensation in gerotor pumps by means of compensation plates.
However, the conventionally known gerotor pumps have the disadvantage that production tolerances lead to a so-called tooth tip play between teeth of the inner rotor and the outer rotor. There is thereby produced a gap particularly between mutually opposing teeth of the inner rotor and the outer rotor. This tooth tip play is already present in the idle state of the pump, that is to say, also while the pump is not operating. During operation of the pump, the pressure increases and further enlarges the gap between the inner rotor and outer rotor so that an inner leakage is caused and the degree of efficiency of the pump decreases.
An object of the invention is to provide a gerotor pump which can reduce a tooth tip play between the inner rotor and the outer rotor during operation by means of radial compensation and thereby has a high degree of efficiency. An object of the invention is further to provide a motor/pump unit which also has a high degree of efficiency.
This object is achieved in particular with a gerotor pump. The gerotor pump is configured and suitable for conveying a fluid from an inlet pump chamber which is connected to an inlet to an outlet pump chamber which is connected to an outlet of the gerotor pump. In this instance, the gerotor pump has a rotatable outer rotor and a rotatable inner rotor. The inner rotor is arranged radially inside the outer rotor. The inner rotor and the outer rotor have rotation axes which are different from each other. The gerotor pump further has a housing having a housing space, in which the outer rotor and the inner rotor are received. Furthermore, the gerotor pump has a plurality of radially displaceable pressure elements. The pressure elements are arranged on an outer circumference of the outer rotor. During operation of the gerotor pump, the pressure elements bear on the housing so that pressure chambers are formed between the outer rotor and housing and/or between the outer rotor and the pressure elements. The pressure chambers are connected in fluid terms to the inlet pump chamber and/or to the outlet pump chamber.
The pressure chambers are during operation of the pump formed between the outer rotor and the housing and/or between the outer rotor and the pressure elements. From these pressure chambers there is produced during operation of the pump a force which presses or urges the outer rotor radially against the inner rotor. This effect is also referred to as “radial compensation”. Consequently, a gap between the outer rotor and inner rotor is reduced, in particular with increasing pressures during operation of the pump, so that the degree of efficiency is increased.
The pressure chambers are advantageously defined as corresponding pressure regions of the fluid which is intended to be conveyed and which are separate or in addition to the pressure regions between the outer rotor and inner rotor through which the fluid is primarily conveyed. In order to differentiate, the pressure regions which are formed between the outer rotor and inner rotor for primary fluid conveying are also preferred to as “primary pressure regions” and the above-defined pressure chambers for radial compensation, which are produced by the pressure elements, are also referred to as “secondary pressure regions”.
In specific embodiments, the gerotor pump has at least two pressure elements. In a particularly preferred manner, the gerotor pump has at least three to seven, more preferably at least eight pressure elements. In a particularly preferred manner, the gerotor pump has precisely eight pressure elements or precisely six pressure elements.
In an advantageous embodiment, the housing has along the inner circumference thereof a plurality of housing openings in which a pressure element is at least partially arranged. The housing openings (also referred to as “openings” below) are advantageously slots and/or holes. Advantageously, the pressure elements bear in each case in a circumferential direction of the housing within the housing opening on the housing. The pressure elements bear on the outer circumference of the outer rotor or are urged or pretensioned against the outer circumference of the outer rotor.
The housing openings are advantageously in each case connected in fluid terms to the inlet pump chamber and/or the outlet pump chamber. In other words, the fluid which is intended to be conveyed reaches the openings. This has the advantage that the pressure elements by means of a hydraulic pressure in the openings during operation of the gerotor pump are urged against the outer rotor in order to consequently form the secondary pressure regions. The provision of the pressure elements in housing openings further has the advantage that adaptations of the inner rotor or the outer rotor are not absolutely necessary, whereby the production of the gerotor pump is simplified.
Advantageously, the gerotor pump has a plurality of resilient elements, wherein the resilient elements are arranged in each case in one of the housing openings. The resilient elements pretension the respective pressure element (in the same housing opening) with respect to the outer rotor. In other words, the resilient element presses the pressure element against the outer rotor.
The resilient elements are advantageously helical springs or leaf springs, wherein different types of resilient elements may be arranged in different housing openings. Furthermore, a plurality of resilient elements may be arranged in a housing opening. For example, two helical springs may be arranged in a housing opening. Alternatively or in other housing openings, a (single) leaf spring may be arranged in the housing opening.
In an advantageous embodiment, the outer rotor has along the outer circumference thereof a plurality of openings in which a pressure element is at least partially arranged in each case. The openings are advantageously slots and/or holes. The openings are in each case connected in fluid terms to the inlet pump chamber and/or to the outlet pump chamber. In other words, the fluid which is intended to be conveyed reaches the openings. This has the advantage that the pressure elements which are between the outer rotor and the housing can be at least partially received by the outer rotor. The structural size of the gerotor pump is thereby advantageously reduced.
The pressure elements are radially displaceable and advantageously at least partially arranged in the above-mentioned openings/housing openings. In a case in which the pressure elements are arranged in openings of the outer rotor, the pressure elements may, for example in the idle state of the pump be arranged completely inside the respective opening and during operation of the pump be displaced radially outward by means of an active centrifugal force in order to be arranged only partially in the respective opening. The pressure elements can during operation of the pump all emerge to the same or a similar degree from the respective opening thereof or emerge to mutually differing degrees from the respective opening thereof.
In a case in which the pressure elements are arranged in housing openings, the pressure elements may, for example, in the idle state of the pump be arranged completely inside the respective opening. During operation of the pump, a hydraulic pressure of the inlet pump chamber and/or the outlet pump chamber which are connected in fluid terms to the opening may urge the respective pressure element against the outer rotor.
In another example, the pressure elements can also by means of the resilient elements be urged or pretensioned against the outer rotor in the idle state of the pump.
In an advantageous embodiment, the housing has a housing cover and a housing base between (in an axial direction) which the inner rotor and the outer rotor are arranged. In the axial direction between the housing cover and the inner rotor and outer rotor and between the housing base and inner rotor and outer rotor there are provided spaces which form portions of the inlet pump chamber and the outlet pump chamber so that the fluid which is intended to be conveyed axially surrounds the inner rotor and the outer rotor.
In preferred embodiments, the housing cover and/or the housing base preferably have grooves which together with intermediate spaces between the inner rotor and the outer rotor form the inlet pump chamber and the outlet pump chamber. The grooves advantageously extend at least partially in a circumferential direction of the outer rotor. In a plan view, defined as a view of a cross section of the outer rotor and the inner rotor perpendicularly to the rotation axes, the grooves are in each case arranged at two sides in a circumferential direction of the inlet and/or the outlet and extend in the circumferential direction away from the inlet and/or away from the outlet. As a result of the grooves, a volume of the inlet pump chamber and/or outlet pump chamber between the housing cover/housing base and the outer rotor and/or inner rotor is advantageously increased, whereby a viscous friction with the fluid can be reduced and consequently surfaces with the necessarily small play/tolerances can be reduced and the degree of efficiency of the pump thereby increases.
In a preferred embodiment, the pressure elements are in each case rotary disks. In this instance, the pressure elements which are in the form of rotary disks are preferably substantially rectangular and plate-like. Advantageously, the rotary disks have rounded corners.
It is further advantageous for at least one housing-side side face of the rotary disks which are arranged in openings of the outer rotor, in particular the housing-side side face which comes into contact with the housing, to be rounded. A friction between the rotary disk and the housing is thereby reduced. It is further advantageous for at least one outer-rotor side face of the rotary disks which are arranged in housing openings, in particular the outer-rotor side face, which comes into contact with the outer rotor, to be rounded. A friction between the rotary disk and the outer rotor is thereby reduced.
Advantageously, a height of the rotary disks in an axial direction of the outer rotor is smaller than a height of the outer rotor or smaller than a height of the housing in an axial direction. In other words, a depth in an axial direction of the opening or the slot or the hole in the outer rotor or in the housing is advantageously greater than a height of the respective rotary disk. This has the advantage that fluid which is intended to be conveyed from the inlet pump chamber on the rotary disk along into the housing space can flow between the outer rotor and housing or into the housing opening with particularly little viscous friction. As a result of an adjustment of the height of the rotary disks, a quantity of fluid which as described above flows on the rotary disk, can be controlled so that a pressure between the pressure chambers produced by the rotary disks can be controlled. In specific embodiments, the rotary disks have different heights or all have the same height.
In most specific embodiments, a height of the rotary disks is 90%, preferably 95%, even more preferably 98%, of the height of the outer rotor or the height of the housing. Preferably, a difference in heights between the outer rotor or the housing and the rotary disks is brought about more than (only) by production tolerances. A particularly good effect of the rotary disks and reduction of the friction can thereby be achieved. Alternatively, the height of the rotary disks may be approximately 50% of the height of the outer rotor or the height of the housing.
The above-mentioned height is in particular intended to be understood to be the (axial) length of the above-mentioned side face on the housing or the above-mentioned side face on the outer rotor.
In an advantageous embodiment, the rotary disks at least partially separate the housing space in a circumferential direction of the outer rotor. During operation, pressure chambers are formed at least between the rotary disks in the circumferential direction. These pressure chambers are preferably formed in addition to the above-explained primary pressure regions (between the inner rotor and outer rotor). These pressure chambers are advantageously formed in the circumferential direction between the rotary disks and in a radial direction between the outer rotor and the housing. During operation of the pump, the fluid pressures in the pressure chambers are advantageously not axially symmetrical with respect to the axial direction or with respect to the rotation axes of the outer rotor and/or the inner rotor. In other words, the pressure which is produced inside the pressure chambers is different between at least some of the pressure chambers. There is thereby advantageously produced a force which urges the outer rotor against the inner rotor so that the gap between them is reduced and the degree of efficiency is thereby increased.
In an advantageous embodiment, the pressure elements are in each case pistons. Advantageously, the respective opening is in the form of a hole in which the respective piston is arranged in a radially displaceable manner. The opening is connected in fluid terms to the inlet pump chamber and/or the outlet pump chamber.
In a case in which the pistons are arranged in the outer rotor, during operation of the pump, the piston is displaced radially inward so that a pressure is applied to the fluid which is located in the opening. This pressure in turn applies a force to the outer rotor which urges the outer rotor against the inner rotor and reduces the gap so that the degree of efficiency is increased. In a case in which the pistons are arranged in the housing, during operation of the pump the piston is displaced radially inward by the pressure applied in the inlet pump chamber or outlet pump chamber so that the piston urges the outer rotor against the inner rotor and reduces the gap so that the degree of efficiency is increased.
Advantageously, the respective piston seals a radially housing-side end of the opening in the outer rotor or seals a radially outer-rotor-side end of the opening in the housing. In other words, each opening in the outer rotor, in which such a piston is arranged has a radially inner end (inner-rotor-side end) and a radially outer (housing-side) end, wherein the piston protrudes in a displaceable manner at least partially out of the housing-side end. A radial inner side of the opening in the outer rotor, which is an inner side of the opening at the radial inner end thereof and which is connected in fluid terms to the inlet pump chamber and/or to the outlet pump chamber forms with the piston a piston pressure chamber. In a case in which the piston is arranged in an opening of the housing, the radially inner end of the opening is arranged at the outer rotor side and the radially outer end of the opening is arranged radially further outward in the housing. The piston pressure chamber is in this instance formed between the radially outer end of the housing opening and the piston which is arranged between the housing and outer rotor.
In other words, the piston and the opening together form a piston/cylinder arrangement. The piston pressure chamber advantageously applies the above-explained application force to the outer rotor so that the degree of efficiency of the pump is increased.
The radially inner end of the opening in the outer rotor or the radially outer end of the housing opening is preferably connected to the intermediate space between the outer rotor and the housing cover or, depending on the axial orientation of the opening, to the intermediate space between the outer rotor and the housing base so that the fluid in this intermediate space can flow into the opening.
Advantageously, the configuration of the pressure elements as a rotary disk and as a piston can be combined. For example, in this instance at least one pressure element is in the form of a rotary disk and at least one pressure element is in the form of a piston. Furthermore, a pressure element may be functionally at the same time in the form of a rotary disk and a piston, for example, by means of a configuration of the rotary disk as a piston with an exemplary height in an axial direction of at least 50% or 90%, or one of the other values mentioned above in relation to the rotary disks, of the height of the outer rotor, Advantageously, in this instance such pistons separate the housing space in the circumferential direction of the outer rotor at least partially and form in the circumferential direction in addition to the piston pressure chambers additional pressure chambers between the outer rotor and the housing.
In an alternative embodiment, the outer rotor and the housing space have center point axes which are different from each other perpendicularly to the radial direction. In this instance, in particular the center point axis of the housing space and the rotation axis of the outer rotor do not correspond to each other. In other words, the outer rotor is not arranged centrally in the housing space. This has the advantage that the secondary pressure chambers are asymmetrical and a force resulting from these pressure chambers urges the outer rotor against the inner rotor so that the degree of efficiency is increased. As a result of the deviating center point axes, during operation of the pump an angular or circumferential position of a maximum produced pressure in the secondary pressure chambers is changed accordingly so that a resulting pressure force from all secondary pressure chambers counteracts the resulting pressure force of the primary pressure chambers which urges the outer rotor. If the pressure force from the primary pressure chambers is more than compensated for (more than completely counteracted), the gap between the outer rotor and inner rotor is reduced, whereby the degree of efficiency can be further increased.
Preferably, the outer rotor has at least one, in particular a plurality of outer rotor groove(s) which are distributed in the circumferential direction. The outer rotor grooves are in particular in each case formed in the circumferential direction between the above-mentioned openings. The outer rotor grooves advantageously reduce a viscous friction with the fluid between the outer rotor and housing cover and/or housing base. The outer rotor grooves may be formed at one or both axial sides of the outer rotor (housing base side and/or housing cover side). The outer rotor grooves are in this instance in particular formed as recesses in the outer rotor which are elongate in the circumferential direction and deep in the axial direction. Preferably, the inner rotor may also have such corresponding grooves (inner rotor grooves).
Preferably, the housing has at least one, in particular a plurality of housing groove(s) which are distributed in the circumferential direction. The housing grooves are in particular in each case formed in the circumferential direction between the above-mentioned housing openings. The housing grooves advantageously reduce a viscous friction with the fluid between the housing and housing cover and/or housing base. The housing grooves may be formed at one or both axial sides of the housing (housing base side and/or housing cover side). The housing grooves are in this instance in particular formed as recesses in the housing which are elongate in the circumferential direction and deep in the axial direction. Preferably, the inner rotor and/or the outer rotor may have such grooves.
In most embodiments, the gerotor pump further has at least one compensation plate which (in each case) is/are arranged in an axial direction between the housing cover and/or housing base and inner rotor and/or outer rotor and enable(s) an axial compensation of the gerotor pump. The gerotor pump thereby advantageously has radial compensation and axial compensation, whereby the degree of efficiency is particularly high.
The invention further relates to a motor/pump unit. The motor/pump unit has a gerotor pump according to one of the above preferred embodiments. Furthermore, the motor/pump unit has a motor which is connected to the inner rotor and which is configured to rotate the inner rotor in order to operate the gerotor pump. The motor is in particular mechanically connected to the inner rotor by means of a shaft. The motor/pump unit has an increased degree of efficiency.
The gerotor pump and the motor/pump unit further have the following advantages. As a result of the compensation of tolerances (radial compensation or radial compensation with axial compensation), the components thereof can be produced at a significantly reduced cost since production tolerances can be significantly expanded. As a result of the higher degree of efficiency, they can be used in higher pressure ranges. Furthermore, as a result of the radial compensation a performance stability over different pressures is increased. Furthermore, for the above-explained radial compensation no additional control is required since the radial compensation functions in a self-controlling manner as a result of a hydraulic operating principle.
The above-explained preferred embodiments and effects are independent of a rotation direction of the outer rotor or the inner rotor.
Other details, advantages and features of the present invention will be appreciated from the following description of exemplary embodiments with reference to the drawings, in which:
The gerotor pump 1 (“pump 1” below) in order to convey a fluid has a rotatable inner rotor 7 and a rotatable outer rotor 6. The inner rotor 7 is in the form of a gear. The outer rotor 6 is in the form of a toothed ring.
The inner rotor 7 and the outer rotor 6 are received in a housing space 11 of a housing 10. In this instance, the inner rotor 7 is arranged in a radial direction 15 within the outer rotor 6.
The inner rotor 7 can be rotated about an inner rotor rotation axis 8, whilst the outer rotor 6 can be rotated about an outer rotor rotation axis 9. As can be seen in
As can further be seen in
The outer rotor 6 has at least two, in this instance eight, openings 16 on the outer circumference 13 thereof. The openings 16 are, as explained below with reference to
A rotary disk 12 is arranged in each opening as a pressure element. The rotary disks 12 can be radially displaced inside the respective openings 16. When the outer rotor 6 is rotated, a centrifugal force which results from the rotation results in the rotary disks 12 protruding from the respective openings 12 and bearing on the housing 12.
As explained below (see
As a result of an eccentric rotation of the outer rotor 6 within the housing space 11, pressure chambers 14 with different fluid pressures are formed. These different fluid pressures at various circumferential locations around the outer rotor 6 produce a resultant force which urges the outer rotor 6 against the inner rotor 7. In this instance, the resultant force advantageously results in the outer rotor 6 being pressed in an illustrated-y direction against the inner rotor 7. A gap between opposing tips 19 of the outer rotor 6 and the inner rotor 7 is thereby advantageously reduced. At the locations of the opposing tips 19, a reduction of the gap between the outer rotor 6 and inner rotor 7 has the greatest advantageous effect of reducing an inner leakage and increasing the degree of efficiency of the pump 1. This is further explained with reference to
Furthermore, the fluid is located partially inside the respective opening 16 radially further inward than the respective rotary disk 12. In this instance, the fluid is located in an opening space 24 between a radially inner side 17 of the opening 16 and the rotary disk 12 so that opening space/pressure chambers 25 are formed. The opening space/pressure chambers 25 ensure a resilience of the rotary disks 12 and, as explained below with reference to embodiment two, another (urging) force of the outer rotor 6. Alternatively or additionally, there may be arranged in the respective opening space 24 a resilient element which pretensions/urges the rotary disk 12 in a resilient or radial manner.
More specifically, the pump 1 has a housing cover 20 and a housing base 21, wherein the housing base 21 is not (directly) visible in the present view. The inner rotor 7 and the outer rotor 6 are arranged, in an axial direction 30 of the outer rotor 6 which coincides with the outer rotor rotation axis 9 (in this instance in the z direction), between the housing cover 20 and the housing base 21. In this instance, at least between the housing cover 20 (and/or at least the housing base 21) and the outer rotor 6 and the inner rotor 7 in the axial direction 30 a spacing (axial gap) is formed so that fluid surrounds the outer rotor 6 and the inner rotor 7.
Openings for an inlet 2 and for an outlet 4 are formed in the housing base 1. The fluid is conveyed by the pump 1 from the inlet 2 to the outlet 4. As can further be seen in
During operation of the pump 1, fluid is conveyed from the inlet 2 to the outlet 4 in the circumferential direction 18. As can be seen in
At the locations of the opposing tips 19, a separation of the volumes 23 and consequently a degree of efficiency of the pump 1 as a result of the small contact surfaces of the teeth is particularly sensitive with respect to production tolerances and with respect to an urging of the outer rotor 6 at high pressures of the fluid. As a result of the urging of the outer rotor 6 against the inner rotor 7, brought about by the rotary disks 12 explained with respect to
Furthermore, the outer rotor 6 has a plurality of outer rotor grooves 26, which are formed in the circumferential direction 18 between the openings 16. As a result of the outer rotor grooves 26, a viscous friction with the fluid between the outer rotor 6 and the housing cover 20 and/or the housing base 21 is reduced.
As can be seen in
As a result of the smaller height 27 of the rotary disk 12, fluid, indicated by a fluid flow 29, can flow particularly easily from the inlet pump chamber 3 on the rotary disk 12 into the housing space 11 between the outer rotor 6 and housing 10. In this instance, in particular the above-mentioned fluid between the housing cover 20 and the outer rotor 6 and inner rotor 7 (in the axal gap) can flow particularly easily into the housing space 11, that is to say, with little viscous friction.
In this instance, the rotary disk 12 further has a rounded side face 31 on the housing, whereby a friction between the rotary disk 12 and the housing 10 is reduced.
In the present embodiment, the pressure elements are in the form of a piston 32. In this instance, the gerotor pump 1 has at least two, in this instance six, pistons 32. The openings 16 are in the form of radial holes in the outer circumference 13 of the outer rotor 6. The pistons 32 are radially displaceable and seal a radially housing-side end 34 of the respective opening 16. Furthermore, the openings 16 are connected in fluid terms to the inlet pump chamber 3 and/or to the outlet pump chamber 5. To this end, the openings 16, as illustrated in
Between the radially inner side 17 of the opening 16 and the respective piston 32 piston pressure chambers 33 are thereby formed. When the outer rotor 6 is rotated, the pistons 32 are pressed radially into the openings 16, wherein the fluid is acted on with pressure by the piston 32. This pressure which is produced applies a force to the radial inner side 17 of the opening 16 and consequently to the outer rotor 6, whereby this rotor is urged against the inner rotor 7. The piston pressure chambers 33 are, in a similar manner to the pressure chambers 14 which are produced by the rotary disks 12, secondary pressure regions.
As shown by comparing
In the above embodiments, the outer rotor 6 is at least in the idle state of the pump 1 not arranged centrally in the housing space 11. Alternatively, however, the outer rotor 6 may in the idle state of the pump 1 be arranged centrally in the housing space 11. In this instance, a pressure difference between the inlet 2 and the outlet 4 (primary pressure regions) during operation of the pump 1 brings about an urging of the outer rotor 6. This urging, in particular at high pressures, further brings about a non-central arrangement of the outer rotor 6 in the housing space 11 so that even in such a case during operation of the pump 1 the secondary pressure regions are formed. However, these secondary pressure regions at least partially counteract the urging by the primary pressure regions so that the gap between the outer rotor 6 and the inner rotor 7 at least during the operation of the pump 1 is reduced and the degree of efficiency thereof is increased.
In the present embodiment, as can be seen in particular in
Each rotary disk 35 protrudes from a radial inner side 39 of the housing opening 37 and is arranged on the outer rotor 6. As can be seen in particular in
As can further be seen in
Preferably, the housing cover 20 or the housing base 21 may have grooves which direct the fluid into the housing opening 37. In this instance, for example, the resilient element 38 may functionally at least partially be replaced by fluid in the housing opening 37 which urges the rotary disk 35 against the outer rotor 6.
Alternatively or additionally to the grooves in the housing cover 20 or in the housing base 21, the housing 10 may have one or more housing grooves 43 which are illustrated with dashed lines in
Furthermore, a plurality of housing grooves 43 may be arranged in the housing 10. In the present example of four openings 37, there may be formed in particular two housing grooves 43 which each connect two of the four openings 37 to each other. It is thereby possible, for example, for two of the openings 37 to be connected in fluid terms to the inlet pump chamber 3 and for the other two of the openings 37 to be connected in fluid terms to the outlet pump chamber 5 without them being short-circuited in fluid terms (in pairs).
The rotary disks 35 of the present embodiment afford the same advantages as the rotary disks 12 of the first embodiment. In other words, the rotary disks 35 produce pressure chambers 14 in the housing space 11 radially between the outer rotor 6 and the housing 10, whereby the outer rotor 6 is urged.
The gerotor pump 1 according to the present embodiment can be combined with the gerotor pump 1 according to the first and/or second embodiment. In this instance, in particular the rotary disks 35 of the present embodiment, with the exception of the fact that they are arranged in the housing 10, and the associated openings 37 thereof may have similar or identical configurations to the pressure elements 12, 32 and openings 16 of the first two embodiments. For example, the present rotary disks 35 may also be in the form of pistons which urge the outer rotor 6 against the inner rotor 7. This combination can particularly advantageously be combined with the above-mentioned configuration, in which the housing 10 has one or more housing grooves 43, additionally or alternatively to the possible grooves in the housing cover 20 or in the housing base 21.
The invention further relates to a motor/pump unit 100. This is illustrated in
The motor/pump unit 100 has a motor 101 and a gerotor pump 1 according to the above embodiments. The motor 101 is configured to rotate the inner rotor 7 to operate the gerotor pump 1. In this instance, the motor 101 is mechanically connected to the inner rotor 7 by means of a shaft 102 (see also
The motor/pump unit 100 has a particularly good degree of efficiency and is less dependent on tolerances.
In addition to the above written description of the invention, for the additional disclosure thereof reference may explicitly be hereby made to the illustration of the invention in the Figures.
| Number | Date | Country | Kind |
|---|---|---|---|
| 102023117788.5 | Jul 2023 | DE | national |
| 102023122127.2 | Aug 2023 | DE | national |
