Patent Application
20230366410
The invention relates to a radial continuous-flow machine, in particular a driven radial-flow machine, for example a radial-flow pump, with cooling and lubrication by means of a medium flowing through the machine, wherein the medium flows from a high-pressure side to a low-pressure side of the radial continuous-flow machine, having a housing assembly and a rotor assembly that is rotatably mounted in an interior of the housing assembly, wherein at least one first bearing is provided for mounting the rotor assembly in the housing assembly, wherein the rotor assembly includes a rotor of an electric motor and an impeller, wherein the motor includes, in addition to the rotor, a stator that is a part of the housing assembly, wherein the rotor of the motor is arranged in a first region of the rotor assembly, and the stator is arranged in a first region of the housing assembly, wherein the first region of the housing assembly encloses the first region of the rotor assembly, wherein a distance that forms a first gap is provided between the first region of the housing assembly and the first region of the rotor assembly, which gap is connected on one side to the high-pressure side and on another side to the low-pressure side of the radial continuous-flow machine, so that a bypass flow of the medium flowing through the radial continuous-flow machine flows through the first gap during operation of the radial continuous-flow machine, and in so doing carries away heat from the rotor and/or the stator of the motor, wherein the first bearing has a second gap that is provided between a first bearing part of the rotor assembly and a first bearing part of the housing assembly, wherein the first gap is connected on the low-pressure side or on the high-pressure side to the second gap, so that a part of the medium flowing through the radial continuous-flow machine flows through the second gap during operation of the radial continuous-flow machine, and in so doing provides for lubrication of the bearing.
Radial continuous-flow machines, in particular such radial-flow pumps, are known to the inventors. They have the advantage that the motor is cooled, and the first bearing is partially lubricated with the aid of the bypass flow flowing through the first gap. If the bypass flow is subsequently routed through the second gap as well, complete lubrication of the first bearing is possible.
If the bypass flow of the medium is routed from the first gap to the second gap, it passes through a region of transition from the first to the second gap. In this region, the bypass flow can be redirected.
Particles that are carried along by the bypass flow can be deposited and accumulate in the first bearing. This can occur, for example, because zones arise in the transition region between the first gap and the second gap in which the flow velocity of the medium is low. The bypass flow can be decreased by deposited particles. This can adversely affect both the cooling of the motor and the lubrication of the first bearing. The deposition of particles should therefore be avoided.
It is therefore an object of the invention to avoid the deposition of particles in the first bearing.
This object is attained according to the invention by the means that bypass orifices or bypass passages are provided in a region of the transition from the first gap to the second gap that connect this region of the transition to the low-pressure side of the radial continuous-flow machine so that only a part of the medium flowing through the first gap also flows through the second gap during operation of the radial continuous-flow machine. Preferably, the greater part of the bypass flow is routed through the bypass orifices or bypass passages. This greater part of the bypass flow then carries along the particles entrained in the bypass flow so that they cannot be deposited in the first bearing. Preferably, the connection of the bypass orifices or bypass passages to the transition region is designed such that the part of the bypass flow routed through the bypass orifices or bypass passages is diverted less often than in the prior art so that fewer zones of low flow velocity can arise in the first bearing as a result. Moreover, the bypass orifices or bypass passages preferably have a cross section that offers a lower resistance to the part of the bypass flow than the second gap, so that the part of the bypass flow flowing through the bypass orifices or bypass passages is greater than the part of the bypass flow flowing through the second gap.
In this way, it is possible that each bypass orifice or each bypass passage has a minimal cross section, and that a length and a width or a diameter of at least one of these minimal cross sections is greater than the distance between the first region of the housing assembly and the first region of the rotor assembly in the region of the second gap.
Furthermore, it is possible that the sum of the minimal cross sections of the bypass orifices or bypass passages is greater than the minimal cross section of the second gap.
In a radial continuous-flow machine according to the invention, the first bearing part of the housing assembly can be composed of an annular groove. The first bearing part of the rotor assembly can be composed of a first ring that projects into the annular groove and is a part of the rotor assembly.
A part of the first gap can be formed between a radially outer boundary surface of the annular groove and a radially outer surface of the first ring. The second gap can be formed between a radially inner boundary surface of the annular groove and a radially inner surface of the first ring. The region of the transition from the first gap to the second gap can be formed between an axial boundary surface of the annular groove and an axial surface of the first ring.
In a radial continuous-flow machine according to the invention, the radially inner boundary surface of the annular groove can be a radially outer surface of a second ring that is a part of the housing assembly. The bypass orifices or bypass passages that connect the region of the transition from the first gap to the second gap to the low-pressure side of the radial continuous-flow machine can be provided in the second ring. The bypass orifices or bypass passages can be, in particular, through-holes that extend radially in the second ring.
The first bearing can be a radial plain bearing. A bearing sleeve of this plain bearing can be a part of the rotor assembly.
Further scope of applicability of the present invention will become apparent from the detailed description given hereinafter. However, it should be understood that the detailed description and specific examples, while indicating preferred embodiments of the invention, are given by way of illustration only, since various changes and modifications within the spirit and scope of the invention will become apparent to those skilled in the art from this detailed description.
The present invention will become more fully understood from the detailed description given hereinbelow and the accompanying drawings which are given by way of illustration only, and thus, are not limitive of the present invention, and wherein the sole FIGURE shows a longitudinal section through a radial-flow pump according to the invention.
The radial-flow pump P shown has a housing assembly 1, a rotor assembly 2, and a control assembly 3.
The housing assembly 1 has a first housing part 11, a second housing part 12, a cover 13, a cap 14, and a stator 15 of an electric motor 15, 25 of the radial-flow pump P.
The first housing part 11 and the second housing part 12 surround a first housing interior, in which the rotor assembly 2 is rotatably arranged by means of a first bearing and a second bearing. The first housing interior has a first region, which is enclosed by a first region 1a of the housing assembly 1. Arranged in this first region 1a of the housing assembly 1 is a first region 2a of the rotor assembly. Arranged in a second region of the housing interior, which is enclosed by a second region 1b of the housing assembly 1, is a second region 2b of the rotor assembly 2.
The first region 1a of the housing assembly is composed of the stator 15 and a part of the first housing part 11 in which the stator 15 is arranged in an outer, circumferential recess. Formed in this first region 1a is a first bearing part of the housing assembly 1, which constitutes a part of the first bearing. A first annular groove is formed for this purpose in a wall of the first housing part 11 located in an axial direction. Rolling elements or other bearing elements that facilitate a rotation can be arranged in the first annular groove. The first annular groove is provided between a radially inner wall of the first region 1a of the housing assembly and a ring 111.
The second region 1b of the housing assembly is composed essentially of a part of the second housing part 12 and only to a small degree of the first housing part 11. Formed in this second region 1b is a second bearing part of the housing assembly 1, which constitutes a part of the second bearing. A second annular groove is formed for this purpose in a wall of the second housing part 12 located in an axial direction. Rolling elements or other bearing elements that facilitate a rotation can be arranged in the second annular groove. The first annular groove and the second annular groove are located on opposite sides of the first housing interior.
The second housing part 12 has an intake connection 121 on the low-pressure side and a discharge connection 122 on the high-pressure side, by which means the medium delivered by the radial-flow pump P can flow into the first housing interior and out of the first housing interior. The intake connection 121 is connected to the first housing interior by an intake passage 123. The first housing interior is connected to the discharge connection 122 by discharge passages 114, 124, 115, 125. The discharge passages 114, 124, 115, 125 in this case are composed of grooves 114, 115 in the first housing part 11 and of grooves 124, 125 in the second housing part 12.
The rotor 2 has two component parts, namely an impeller 21 and a rotor 25 of the electric motor 15, 25. The impeller 21 is a hollow shaft whose ends 212, 213 form rings that are rotatably arranged in the first or in the second annular grooves, respectively, of the housing assembly 1. The first ring 212 of the impeller projecting into the first annular groove forms a first bearing part of the rotor assembly 2, and the second ring 213 of the impeller projecting into the second annular groove forms a second bearing part of the rotor assembly 2. Together with the first bearing part and the second bearing part of the housing assembly, they form the first and second bearing, respectively.
The first region 2a of the rotor assembly has the rotor 25 of the motor 15, 25. This is placed in an outer, circumferential recess of an impeller 21.
The second region 2b of the rotor assembly 2 forms a runner with runner blades 211. The intake passage 123 opens into the center of this runner between the runner blades 211. It forms a low-pressure side of the radial-flow pump P.
Owing to the rotation of the rotor assembly 2, and thus of the runner blades, the inflowing medium is forced into the discharge passages 114, 124, 115, 125. The pressure of the medium is increased as a result. The discharge passages 114, 124, 115, 125 are arranged on a high-pressure side of the radial-flow pump P.
Between the first region 2a of the rotor assembly 2, including the first ring 212, and the first region 1a of the housing assembly 1, a first gap that extends into the first annular groove is provided between a radially outer surface of the first region 2a of the rotor assembly 2 and a radially inner surface of the first region 1a of the housing assembly 1. On the side opposite the first annular groove, the first gap is connected to the high-pressure side of the radial-flow pump P, namely to at least one of the discharge passages 114, 124, 115, 125.
Formed between a radially inner surface of the first ring 212 and a radially inner boundary surface of the annular groove is a second gap. The radially inner boundary surface of the annular groove is a radially outer surface of the ring 111 that is a part of the housing assembly and projects from the wall of the first housing part 11 located in an axial direction. On the side opposite the first annular groove, the second gap is connected through a hollow space in the impeller to the low-pressure side of the radial-flow pump, namely the center between the runner blades 211.
A transition region U that connects the two gaps S1, S2 is provided between the first gap S1 and the second gap S2. This transition region U is formed between an axial boundary surface of the annular groove and an axial surface of the first ring 212.
It is not solely through the second gap S2 that the transition region U is connected to the low-pressure side of the radial-flow pump P. Instead, bypass passages are provided in the ring 111 of the first housing part that connect the transition region U to the low-pressure side of the radial-flow pump P through the interior of the impeller. The bypass passages have a cross section that is greater than the second gap S2.
The control assembly 3 is arranged in the second housing interior, which is surrounded by a part of the second housing part 12, the cover 13, and the cap 14.
The control assembly 3 has a circuit board 31, on which various electrical components 32 are arranged. These electrical components 32 and conductive traces on the circuit board 31 form an electrical circuit with which the motor 15, 25 is controlled and supplied with power. The radial-flow pump has a plug connector, of which one part 131 is an integral part of the cover 13. Electrical contacts of the plug connector are connected to the circuit.
During operation of the radial-flow pump P, the runner is driven and in this way the inflowing medium is pumped to the discharge connection 122. At the high-pressure side, a bypass flow is branched off from the pumped medium and is routed through the first gap S1. This bypass flow provides for a cooling of the electric motor 15, 25. The bypass flow flows through the transition region U. From the transition region U, a smaller part flows through the second gap, where it provides for lubrication in the first bearing. A greater part of the bypass flow flows through the bypass orifices, past the second gap, to the low-pressure side. This greater part of the bypass flow travels along with particles that are transported in the bypass flow, thereby preventing them from being deposited in the transition region U or in the second gap and thus causing damage to the bearing.
The invention being thus described, it will be obvious that the same may be varied in many ways. Such variations are not to be regarded as a departure from the spirit and scope of the invention, and all such modifications as would be obvious to one skilled in the art are to be included within the scope of the following claims.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2021 102 149.9 | Jan 2021 | DE | national |
This nonprovisional application is a continuation of International Application No PCT/EP2022/050727, which was filed on Jan. 14, 2022, and which claims priority to German Patent Application No 10 2021 102 149.9, which was filed in Germany on Jan. 29, 2021, and which are both herein incorporated by reference.
| Number | Date | Country | |
|---|---|---|---|
| Parent | PCT/EP2022/050727 | Jan 2022 | US |
| Child | 18227684 | US |
