Patent Application
20240151229
The invention lies in the field of positive-displacement machines according to the spiral principle and relates to a scroll machine, in particular in the form of a scroll compressor, preferably as an electrical refrigerant drive, in particular as a refrigerant compressor for refrigerant of a vehicle air-conditioning system.
Motor vehicles are generally fitted with air-conditioning systems which control the climate inside the vehicle interior with the aid of a system forming a refrigerant circuit. Systems of this kind have, in principle, a circuit in which a refrigerant is guided. The refrigerant, for example R-744 (carbon dioxide, CO2) or R-134a (1,1,1,2-tetrafluoroethane), is heated at an evaporator and compressed by way of a (refrigerant) compressor. The refrigerant subsequently releases the absorbed heat via a heat exchanger before being guided back to the evaporator via a throttle valve.
As refrigerant compressor, use is often made of what is known as a scroll machine in order to compress a refrigerant. The construction and the functioning of such a scroll machine, used as compressor for the refrigerant of a motor vehicle air-conditioning system, is described, for example, in DE 10 2012 104 045 A1 and its counterpart U.S. Pat. No. 9,945,380 B2. Essential elements of such a scroll compressor are two scroll parts (“scrolls”) that are movable relative to one another. The system usually also contains oil in droplet form or as a mist, which after the compression is at least partially separated from the refrigerant (which is usually gaseous after the compression). The refrigerant (possibly with oil residues) is then introduced into the air-conditioning circuit, whereas the separated-off oil can usually be led within the scroll machine to moving parts for lubrication of same. The scroll parts are generally embodied as a stationary, fixed scroll (fixed scroll, displacer scroll) and as a movable, orbiting scroll (mating scroll, rotor scroll). The two scrolls are fundamentally of identical construction and each have a base plate (main body, scroll disk) and a spiral-shaped (worm-shaped) wall (spiral wall, scroll wall) extending from the base plate in an axial direction. In the assembled state, the spiral walls of the two scrolls lie nested in one another and form multiple conveying chambers between the partially contacting scroll walls.
To drive the movable scroll, an electric motor is typically provided, the motor shaft of which (D-side, i.e., drive side) is coupled in terms of drive to the movable scroll part by means of an eccentric shaft journal (also: “shaft pin”).
Here and in the following text, the expression “orbiting” movement should in particular be understood to mean an eccentric, circular movement path, in the case of which the movable scroll itself does not rotate about the dedicated axis. During operation, the two scrolls have the smallest possible axial spacing from one another, wherein, during each orbiting movement, substantially sickle-shaped (compressor or conveying) chambers are formed between the spiral walls, the volume of said chambers moving, in the course of the movement of the two scrolls relative to one another, (at least in a compression process) from the outer side along the spiral walls in the direction of the center axis of the respective scroll and in so doing being increasingly reduced (and thus the medium guided therein is compressed).
Here, the orbiting movement of the movable scroll is usually effected, inter alia, by means of an anti-rotation mechanism which prevents the intrinsic rotation of the scroll. That mechanism is usually switched between the movable scroll and a positionally fixed element of the scroll machine. The anti-rotation mechanism is often formed by a number of circular, pocket-like openings (“rings”) arranged on a circular path, usually in the movable scroll, and assigned “pins”, usually arranged in the positionally fixed element. In this case, the pins engage into the circular openings in the movable scroll, and in each case form what is known as a pin-ring contact. During (compressor) operation, the pins slide along the circular opening walls, as a result of which an intrinsic rotation is prevented. To reduce friction and improve the service life, for example running rings (sliding rings) are inserted into the openings. On account of this design, the anti-rotation mechanism is also referred to as “pin-ring system”.
The motor shaft is generally mounted in an end shield (also referred to as “central plate” or “center plate”) by means of a bearing. The pins of the anti-rotation mechanism are thus usually fixed (in particular force-fittingly) in the end shield.
By way of example, such anti-rotation mechanisms have six such pin-ring contacts. Here, the pin-ring contacts are in particular arranged offset by 60° relative to one another.
It is recognized that such anti-rotation mechanisms have a high number of components, as a result of which the production and mounting of the scroll machine is comparatively complex and expensive.
It is accordingly an object of the invention to provide a scroll machine, such as a scroll compressor, which overcomes a variety of the disadvantages associated with the heretofore-known devices and methods of this general type and which provides for an improved scroll machine and a correspondingly improved air-conditioning system for a motor vehicle.
With the above and other objects in view there is provided, in accordance with the invention, a scroll machine, comprising:
The scroll machine according to the invention serves in particular as a compressor for refrigerant of a vehicle air-conditioning system. In this case, the scroll machine comprises a first scroll with a first base plate and with a first spiral wall which projects (in particular axially) from the first base plate. Here, the first spiral wall is designed so as to follow a first spiral line (i.e., assigned in particular to the first scroll) and forms a first spiral passage. In particular, the first scroll also has a peripheral delimiting wall. The scroll machine also comprises a second scroll with a second base plate (i.e., assigned in particular to the second scroll) and with a second spiral wall which projects (in particular axially) from the second base plate. The second spiral wall is designed so as to follow a second spiral line and engages into the first spiral passage of the first scroll. In this case, during intended operation, the second spiral wall together with the first spiral wall forms, in particular due to common contacts (in particular on account of an eccentric arrangement relative to one another), a number of conveying chambers (which move in particular along the first spiral wall) (also referred to as “compressor chambers” during an intended compressor operation). The first and the second spiral wall also each have in certain regions on the inner wall surface thereof and the outer wall surface thereof a wall surface profile which is superposed (in particular azimuthally) on the respective spiral line and is matched to the facing wall surface profile of the respectively other spiral wall. Here, this respective, superposed wall surface profile is designed in such a way that, during intended operation, a contact normal of a contact point of one of the two spiral walls (for example the first spiral wall) is produced at least in certain regions and this contact normal is positioned obliquely in relation to a local normal (i.e., positioned in particular at the position of the contact point) of the corresponding first or second (in the present example with respect to the first) spiral line. Preferably, the contact force (in particular the vector thereof or the direction thereof) is at the point at which both spiral walls contact one another, obliquely with respect to the normal of the spiral line at this position.
Thus, the contact normal produced on account of the superposed wall surface profiles is also positioned obliquely in relation to a contact normal of two “ideal spiral walls”—i.e., in particular conventional scroll walls.
Here, “axially” is understood to mean a direction parallel to (coaxial with) an axis of rotation (axial direction) of the scroll machine. In particular, this axial direction is oriented parallel to an axis of rotation of a drive, preferably of an electric motor, which drives at least one of the above-described scrolls, that is to say also perpendicular to the base plates of the two scrolls. “Radially” or “radial direction” is correspondingly understood to mean a direction perpendicular (transverse) to the axis of rotation of the scroll machine. “Azimuthally” or “tangentially” is in particular understood to mean a direction along the periphery of the scroll machine, for example with respect to the possibly present delimiting wall of the first scroll (also referred to as “peripheral direction”, “azimuthal direction” or “tangential direction”), that is to say a direction perpendicular to the axial direction and to the radial direction.
Here and in the following text, “contact point” is in particular understood to mean a contact point, usually a local contact line containing this contact point, at the position of the respective spiral wall at which both spiral walls are understood during intended operation. It is optionally also a contact surface, for example on account of manufacturing tolerances or on account of a contact region which is optionally azimuthally enlarged by the superposed wall surface profile.
Preferably, both scrolls are mounted offset parallel to one another by an eccentric radius. In this case, at least one of the two scrolls is mounted eccentrically with respect to the aforementioned axis of rotation.
On account of the contact normal positioned obliquely with respect to the local normal of the corresponding spiral line, an azimuthal form-fitting engagement between the two spiral walls is made possible, which in turn results at least in inhibition of rotation, preferably blocking of a rotation of the first and/or the second scroll in relation to the respective other and/or about an axis of rotation of the corresponding scroll (in particular thus the intrinsic rotation described in the introduction). In the theoretical ideal state of spiral walls in the form of “true” spirals, these would contact one another at a contact normal that is normal to the respective spiral line, such that a rotation cannot be prevented merely on account of frictionally locking engagement and thus with low security or on account of non-sufficient contact forces. In addition, an (in particular radial) tolerance compensating element which is also described in the introduction, in particular the “swing link”, is often used and allows a slight radial displacement of the scrolls relative to one another in order to improve the fit of the spiral walls against one another. However, here, the gap between the first and second spiral wall can also be increased slightly at least in certain regions (“radial de-osculation”), which would in turn impair or even cancel the friction-related inhibition. In the prior art, the intrinsic rotation should be prevented by an anti-rotation mechanism described in the introduction. By contrast, the configuration according to the invention of the first and second spiral walls, thus in particular the wall surface profiles superposed on the spiral line, already itself permits an (as described above, in particular form-fitting) inhibition of the intrinsic rotation and thus makes it possible to be able to omit a conventional anti-rotation mechanism. It is thus advantageously possible for the number of components and thus also the weight of the scroll machine and in particular also installation space to be reduced.
Optionally, the respective wall surface profiles are also selected in such a way that what are known as the osculating radii of the two spiral walls are adapted to one another. Here, “osculating radius” is in particular understood to mean the local radius in the region of the contact point of the respective spiral wall. In the case of greatly different osculating radii, there is thus also a contact point approximated to the linear or point contact in the tolerance-afflicted manufacturing state, whilst there is instead an areal contact in the case of osculating radii approximated to one another. This can in turn result in a lower loading of the two spiral walls since the contact force between the two scrolls is distributed over a greater surface area.
Thus, the respective superposed wall surface profile possibly also results locally in a contact region extended over a greater angular range than a contact region between two spirals. In this case, a gap length between the two spiral walls is also extended, such that a sealing action in the azimuthal or tangential direction can be improved.
Here and in the following text, “form-fitting engagement” between two parts, which is also referred to as a “positive engagement” or a “form fit,” is in particular understood to mean that a relative movement of these two parts relative to one another is prevented at least in one spatial direction by a direct mutual abutment of contours of the parts themselves. The above-described inhibiting or blocking of the intrinsic rotation in this direction, that is to say in the azimuthal or tangential direction, is thus effected in a shape-related manner.
Here and in the following text, “so as to follow a spiral line” is in particular understood to mean that a “neutral axis”, in particular a type of line of symmetry or center line, of the respective spiral wall is described by the spiral line. Preferably, each of the first and second spiral lines is an “Archimedean spiral.” To increase the mechanical strength, a wall thickness usually increases from the outside (“inlet side”) inward (i.e., in the direction of the spiral center). This is for example achieved in that the respective wall surfaces are arranged offset relative to the spiral line with an “offset” (also: spacing) that increases toward the spiral center. Thus, the pitch of the spiral is slightly steeper for the radially “inner” wall surface than for the spiral line, whereas it is flatter for the “outer” wall surface. The spacing of the inner and the outer wall surface to the neutral axis thus increases in the direction of the spiral center. By contrast, in the case of the present invention, the corresponding wall surface of the respective spiral wall follows the superposed profile in certain regions. However, here, the wall thickness of the respective spiral wall preferably also increases toward the spiral center considered as a whole.
Here and in the following text, the term “superposed” should be understood to mean that the fundamental profile of the first and second spiral walls still follows the assigned spiral line, but locally deviates therefrom—more than by the above-described offset.
The second spiral wall in particular also forms a spiral passage in which the first spiral wall is inserted in the intended mounting state.
In one variant, the scroll machine is designed in such a way that, during intended operation, one of the two scrolls orbits about the other relative thereto. Here, preferably, one of the two scrolls, in particular the first, is positionally fixedly mounted, while the other, in particular the second, is movably mounted. In this case, as described above, the scroll contour according to the invention serves to inhibit the intrinsic rotation, i.e., in order to allow the second scroll to orbit.
In an alternative variant, the two scrolls of the scroll machine are in the form of what are known as “co-rotating” scrolls. In this case, both scrolls rotate in the same direction of rotation about their respective axis of rotation. In both variants, the conveying chambers move in the direction of the spiral center. In this alternative variant, the scroll contour according to the invention may advantageously be used to the extent that only one of the scrolls is driven and it “drags along” the other scroll on account of the form-fitting inhibition of rotation. In other words, the rotation of the one scroll is “transmitted” to the other scroll.
For easier understanding, reference is made below to the orbiting variant and one of the two scrolls, specifically the second scroll, is referred to as orbiting scroll (also: “O-scroll”). In this case, the other, specifically first scroll is preferably referred to as fixed scroll (also: “F-scroll”). However, the following embodiments are equally also applicable to co-rotating scrolls.
In an expedient embodiment, due to the respective wall surface profile, a type of toothing of the first spiral wall with the second spiral wall is formed during compressor operation. Here, it is recognized that the “more significant” the form of the individual “teeth”, the higher the inhibiting or blocking action in relation to the intrinsic rotation too (or alternatively the “carrying-along action” in relation to the non-driven scroll in the case of the co-rotating scrolls). Equally, it is also possible here for radial displacements to be comparatively well compensated by the radial tolerance compensating element mentioned above. In this case, “significance” is in particular understood to mean a radial “height” which deviates from the remaining or at least adjoining region of the wall surface profile and which is preferably measured as the spacing of the wall surface to the aforementioned spiral line, in particular the “neutral axis”, in particular a value of this “height” that lies above a reference value. It is optionally also possible for the significance to be understood as a ratio, lying above a reference value, of this value to a radius (what is known as the “orbiting radius”) with which the two scrolls orbit about one another, in particular the O-scroll about the F-scroll, or to an (in particular average) wall thickness of the corresponding spiral wall.
In a preferred embodiment, the respective wall surface profile of the two spiral walls is of continuous design. In particular, the wall surface profile thus has no discontinuities such as bends, corners, steps or the like. As a result, it is possible to avoid dead spaces when the spiral walls are sliding against one another, said dead spaces at least theoretically being able to lead to an “over-compression” of enclosed fluid or to a type of cavitation or vacuum formation.
In an expedient embodiment, the respective wall surface profile is formed by a superposition of the respective spiral line with a sinusoidal wave shape. This embodiment thus already results in a continuous wall surface profile. In this case, a “wave crest” would thus form a “tooth” of the wall surface profile.
In an alternative embodiment, the respective wall surface profile is formed by a superposition of the respective spiral line with an, in particular rounded and expediently continuous, polygonal profile. Here, “rounded” polygonal profile is in particular understood to mean that the “corners” thereof are of rounded design. In this case, the intrinsically rectilinear portions between the corners are also slightly rounded (this can occur for example on account of the superposition). Alternatively or optionally also additionally (for example depending on the length of the intrinsically rectilinear portion), the respective wall thickness profile here has at least virtually rectilinear portions between the (rounded) “corners” of the polygonal profile that then form the “teeth.”
To form the superposed wall surface profile, for example the curve profile to be superposed (that is to say for example the sinusoidal wave profile or the polygonal profile) is subtracted from the spiral line or added thereto, optionally taking account of the intended wall thickness of the respective spiral wall.
In a further expedient embodiment, mutually facing wall surface profiles of the first and second spiral wall are matched to one another taking account of the orbiting radius. This advantageously enables unimpeded but still sealing sliding of the two spiral walls against one another. Here, the matching to one another taking account of the orbiting radius is fashioned in particular in the case of a projection (seen at least relative to the surrounding regions of the wall thickness profile) of one of the wall surface profiles in such a way that an indentation—corresponding in particular to the projection—of the facing wall surface profile is enlarged in terms of its extent in relation to the projection by the orbiting radius. This projection (that is to say a “wave crest” or the above-described “tooth” in the case of the superposed sinusoidal wave shape) thus meshes in an indentation (or: wave trough or “erosion”), which is enlarged in relation to itself by the orbiting radius, of the opposite spiral wall, regardless of whether the projection is arranged on the outer side or inner side with respect to the corresponding spiral wall. Illustrated in numerical values in exemplary fashion, a partially circular projection, which rise from the “ideal” (or conventional, smooth) spiral profile of the wall surface with a radius of, for example, 0.5 millimeters, would thus be assigned an indentation in the opposite wall surface with a radius of 0.5 millimeters plus the orbiting radius. In addition, this indentation is shaped in the region at which the one spiral wall “touches” the other spiral wall with the projection during compressor operation. As a result, this projection can slide through the indentation without jamming.
In a further expedient embodiment, the radial extent (that is to say in particular the aforementioned height) of such a radial projection or the (“depth”) of a corresponding indentation in the corresponding wall surface profile resulting from the superposition of the corresponding spiral line is limited to a predefined dimension, in particular so that no jamming and/or damage to the scrolls occurs. Here, this dimension is preferably defined by a ratio of the radial extent to the wall thickness, for example in such a way that a residual wall thickness of at least 50 to 60 percent remains at the corresponding point. It is optionally possible to predefine that the aforementioned “neutral axis” is not intersected. By way of example, in particular an indentation must not occupy more than 20 to 25 percent of a “smooth” wall profile in the direction of the neutral axis.
In a preferred embodiment, in the region of the superposed wall surface profiles, the respective contact region between the first and the second spiral wall extends over an angular range of approximately (i.e., in particular +/−2 degrees) 10 to 30 degrees, in particular of 15 to 20 degrees. The contact region thus shortens in the direction of the spiral center, i.e., the azimuthal length thereof becomes smaller.
In an advantageous embodiment, the superposed wall surface profiles do not extend over the entire length of the respective spiral wall, but at least over an angular range of 360 degrees. As a result, at least one “revolution” of the respective spiral wall with the superposed wall surface profiles is provided. This is advantageous to the effect that, as a result, the spiral walls with their superposed wall surface profiles bear against one another at at least two points, such that the inhibiting or blocking action in relation to the intrinsic rotation is increased. Preferably, the superposed wall surface profiles here extend from an inlet of the first spiral passage or of the corresponding spiral wall (that is to say in particular from an outer end of the respective spiral wall) in the compression direction, i.e., toward the spiral center. In particular, the spiral center of the first and the second spiral wall, said spiral center preferably covering an angular range of at least 90 degrees (proceeding from the inner end of the respective spiral wall) up to 180 or 270 degrees, remains free from the respective superposed wall surface profile. The fact that the spiral center remains free from the superposed wall surface profiles advantageously prevents jamming of the spiral walls, possibly on account of manufacturing tolerances, from occurring in this region on account of the required shortening of the wavelength of the sinusoidal profile (or of the polygonal profile) and thus also increasingly “steeper” projections (teeth). Contact between the spiral walls at the obliquely positioned contact normals as far outward on the respective spiral as possible is also advantageous, since then the contact forces for preventing the intrinsic rotation are comparatively small on account of a large lever arm (in relation to the center of rotation). By way of example, a ratio of superposed wall surface profile to “smooth” wall surface profile (i.e., a “conventionally” shaped spiral wall without superposed wave profile or polygonal profile) of approximately 1:3 is sought, that is to say for example one spiral turn with the superposed wall surface profile to three spiral turns without the superposed wall surface profile. The inlet is optionally also free from the superposed wall surface profile and only a portion of the respective spiral wall between the outer end and the inner end is provided with the superposed wall surface profile.
The vehicle air-conditioning system according to the invention comprises the above-described scroll machine. Thus, in corresponding embodiments according to the invention or expedient embodiments, the vehicle air-conditioning system also has all the above-described features and the advantages thereof as well.
Here and in the following text, the conjunction “and/or” should in particular be understood to mean that the features linked by this conjunction may be implemented both jointly and as alternatives to one another. The same meaning is assigned to the expression “at least one of A or B.”
Other features which are considered as characteristic for the invention are set forth in the appended claims.
Although the invention is illustrated and described herein as embodied in a scroll machine and vehicle air-conditioning system, it is nevertheless not intended to be limited to the details shown, since various modifications and structural changes may be made therein without departing from the spirit of the invention and within the scope and range of equivalents of the claims.
The construction and method of operation of the invention, however, together with additional objects and advantages thereof will be best understood from the following description of specific embodiments when read in connection with the accompanying drawings.
Mutually corresponding parts and dimensions are provided with the same reference designations throughout the figures.
Referring now to the figures of the drawing in detail and first, in particular, to
The scroll compressor 2 also has a fixed scroll rigidly fastened in the housing 4 (referred to as “F-scroll 14”). Each of the two scrolls 6, 14 has a worm-shaped or spiral-shaped spiral wall (scroll spiral) 6a, 14a. These are each designed so as to follow an assigned spiral line 6b, 14b (see
During operation, a gas-oil mixture is increasingly compressed due to the change in volume of the compressor chambers 16, as a result of which radial, azimuthal (tangential) and axial fluid forces act on the scroll parts 6, 14. In
In order to be able to better absorb the radially inwardly increasing pressure, the spiral wall 6a and the spiral wall 14a are formed with a wall thickness that increases inwardly toward the spiral center.
Between the delimiting wall 14e and the spiral outer side of the spiral profile of the spiral wall 14a, a radial chamber closure 22 is customarily provided, which extends from the inlet 18a in the spiral direction to the inlet 18b. As is apparent in particular in the plan view of
Referring now to
A housing subregion of a drive housing 38 of the scroll compressor 2 is in the form of a motor housing 38a for receiving an electric motor (not shown in any more detail) and is closed on the one side by an integrated housing intermediate wall (not shown) to an electronics housing 38c which is provided with a housing cover 38b and which has a set of motor electronics (electronics) 40 controlling the electric motor and on the other side by the mechanical interface 30 with the end shield. The drive housing 38 has, in the region of the electronics housing 38c, a connection portion 42 with motor connections 42a and 42b, guided to the electronics 40, for the electrical contacting of the motor electronics 40 to an on-board electrical system of the motor vehicle.
The drive housing 38 has a refrigerant inlet or refrigerant feed 44 for connection to the refrigerant circuit and a refrigerant outlet 46. The outlet 46 is integrally formed on the bottom of the above-described (compressor) housing 4 of the compressor module 28. In the connected state, the inlet 44 forms the low-pressure side or suction side (suction-gas side) and the outlet 46 forms the high-pressure side or pump side of the scroll compressor 2.
Between the O-side end shield and the O-scroll 6, a counterpressure chamber (backpressure chamber) 50 is located in the intermediate wall 32 formed by the end shield (see
The compressed mixture of refrigerant and oil is conducted via the central outlet 20 in the base plate 14c of the fixed F-scroll 14 into a high-pressure chamber 52 (see
In order to then prevent the above-described intrinsic rotation of the O-scroll 6, according to the invention, as illustrated in
In the exemplary embodiment illustrated, the wall surface profiles 68 are formed in that a sinusoidal wave shape is superposed on the contour—and thus also the respective spiral line 6b and 14b—of the wall surfaces 60, 62, 64, 66. The roughly radially oriented projections 71 produced here by the “wave crests” form a type of “tooth” which, during intended compressor operation, slides on the inner side of the spiral wall 6a or 46a in the region of a corresponding recess 72 (a wave trough). It has been found that this increases a form-fitting engagement for the avoidance of the intrinsic rotation. In the present exemplary embodiment, such contact points between the two spiral walls 6a, 14a are present at two such points.
As is also apparent in
The wall surface profiles 68 of the respective mutually facing wall surfaces, that is to say of the wall surfaces 60 and 66 and of the wall surfaces 62 and 64, are also matched to one another. The respective recess 72 is thus designed to be larger, for example with a greater radius, so that the respectively assigned projection 71 (of the other spiral wall 6a or 14a) can slide therein. The dimensions of the recesses 72 differ here by the orbiting radius from the dimensions of the corresponding projections 71, specifically are enlarged by the orbiting radius. Here, the (dimensions of the) individual projections 71 are selected in such a way that the correspondingly enlarged recesses 72 do not reach as far as the spiral lines 6b, 14b.
The respective superposed wall surface profile 68 also extends merely over an angular range of approximately 360 degrees from a “free” or outer end of the respective spiral wall 6a or 14a in the direction of the spiral center. As a result, on the one hand, for a full revolution, a “fit” of the two spiral walls 6a and 14a against one another that prevents the intrinsic rotation is made possible, and, on the other hand, a situation is avoided in which, on account of the increasing curvature of the respective spiral wall 6a or 14a, the wavelength of the sinusoidal wave shape would be shortened and thus also the “relative” tooth height of the projections 71 would be increased, which is undesirable. Furthermore, by way of the projections 71 and recesses 72 being arranged on the outer side, a comparatively large lever arm can be used in order to prevent the intrinsic rotation by means of the form-fitting contacts.
It is recognized that a region specifically of the spiral wall 14a, in the region in which no contact by the O-scroll 6 can be effected on the outer side, does not need to be equipped with the wall surface profile 68 on the outer side.
It will be understood that the subject matter of the invention is not limited to the exemplary embodiments described above. Rather, other embodiments of the invention may be derived from the preceding description by a person skilled in the art. In particular, the individual features of the invention that are described on the basis of the various exemplary embodiments and the design variants thereof may also be combined with one another in some other way.
The following is a summary list of reference numerals and the corresponding structure used in the above description of the invention:
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2021 207 740.4 | Jul 2021 | DE | national |
This application is a continuation, under 35 U.S.C. § 120, of copending International Patent Application PCT/EP2022/069877, filed Jul. 15, 2022, which designated the United States; this application also claims the priority, under 35 U.S.C. § 119, of German Patent Application DE 10 2021 207 740.4, filed Jul. 20, 2021; the prior applications are herewith incorporated by reference in their entirety.
| Number | Date | Country | |
|---|---|---|---|
| Parent | PCT/EP2022/069877 | Jul 2022 | US |
| Child | 18415173 | US |
