METHOD FOR CONTROLLING AT LEAST ONE RADIAL BLOWER IN A COOLING SYSTEM, AND RADIAL BLOWER

Abstract

A method for controlling at least one radial blower in a cooling system, wherein the radial blower comprises a housing in which a shaft is rotationally mounted, which receives at least one impeller wheel of a compressor at one end, which is secured to the housing, and the housing comprises at least one radial bearing and at least one axial bearing via which the shaft is rotationally mounted in the housing, and said radial blower also comprises a motor which is driven by a rotor and a stator and which drives the shaft, wherein, by means of at least one laser Doppler vibrometer assigned to the shaft, operating points of the shaft are detected and forwarded to a controller for determining an operating status of the radial blower.

Claims

1. A method for controlling at least one radial blower in a cooling system, in which the radial blower comprises a housing in which a shaft is rotatably mounted which, on one end, receives at least one impeller of a compressor, which is fixed on the housing, and the housing comprises at least one radial bearing and at least one axial gas bearing, by means of which the shaft) is rotatably mounted in the housing, and an engine driven by a rotor and stator, said engine driving the shaft, wherein operating points of the shaft are detected by at least one vibrometer, which is allocated to the shaft, and are forwarded on to a controller for ascertaining an operating state of the radial blower).

2. The method according to claim 1, wherein a critical threshold value is recognised by the controller of the radial blower, and exceeding the threshold values is prevented by the controller of the radial blower itself or alternatively by the controller of the cooling system.

3. The method according to claim 1, wherein operating points are detected by several radial blowers provided in a cooling system by means of the respective at least one vibrometer, and the respective operating points are compared to one another and set to the maximum energy efficiency of the respective radial blower.

4. The method according claim 1, wherein several radial blowers are connected to one another in the cooling system with a network of data lines, in particular a bus system, for exchanging data.

5. The method according to claim 1, wherein one of the radial blowers is operated as the master and the further radial blowers as slaves.

6. The method according to claim 1, wherein the signals detected by the vibrometer are permanently evaluated, and the respective radial blower is constantly monitored.

7. A radial blower, in particular for a cooling system, comprising: a housing in which a shaft is rotatably mounted which, on one end, receives at least one impeller of a compressor, which is fixed on the housing, at least one radial bearing and having at least one axial gas bearing by means of which the shaft is rotatably mounted in the housing, an engine driven by a rotor and a stator, said engine driving the shaft, wherein at least one vibrometer is provided which is allocated to the shaft.

8. The radial blower according to claim 7, wherein the vibrometer is aligned radially to the shaft.

9. The radial blower according to claim 7, wherein the at least one vibrometer is allocated to the shaft between the rotor of the engine and the radial baring or axial gas baring arranged adjacently thereto.

10. The radial blower according to claim 7, wherein the further vibrometer is allocated to an end-face end of the shaft.

11. The radial blower according to claim 7, wherein the at least one vibrometer is positioned in a housing opening of the housing and is provided in the housing opening in a pressure medium-tight manner.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0020] The invention and other advantageous embodiments and developments thereof are described and explained in more detail below by means of the examples depicted in the drawings. According to the invention, the features that can be seen in the description and the drawings can be applied individually or together in any combination. Here are shown:

[0021] FIG. 1 a schematic sectional view of a radial blower,

[0022] FIG. 2 a schematically enlarged view of an axial gas bearing adjacent to the compressor, and

[0023] FIG. 3 a schematic view of a cooling system.

DETAILED DESCRIPTION

[0024] In FIG. 1, a schematic sectional depiction of a radial blower 11 is depicted. By means of this radial blower 11, a coolant is radially accelerated by at least one impeller 16, 26 of a compressor 27 and led in lines of a cooling system 1, which is depicted by way of example in FIG. 3.

[0025] By means of this radial blower 11, the coolant is radially accelerated by at least one impeller 16, 26 of a compressor 27 and guided in a compressed state into the gas pressure line 75 (FIG. 3) of the compression side of the cooling system 1. The impeller 16, 26 rests on a shaft 17 which is driven in the central region of the engine housing 21 by an engine 20. This engine 20 consists of a rotor 18 connected to the shaft 17 and a stator 19 fixed on the engine housing 21. The region which is arranged outside of the impeller 16, 26 when seen from the shaft 17 forms the pressurise side of the blower. In the upper and lower region of the shaft 17, in each case a radial bearing 22, 23, in particular a lower radial gas bearing 22 and an upper radial gas bearing 23, are arranged. These radial gas bearings 22, 23 comprise stationary bearing surfaces which are referred to as the radial stator 24. Furthermore, the shaft 17 comprises rotating bearing surfaces 25 in the region of the radial gas bearings 22, 23. The pressure medium for the gas bearing is advantageously the coolant. An axial gas baring 31 is provided between the impeller 16 of the compressor 27 and the lower radial gas bearing 22. This axial gas bearing 31 comprises a rotating plate 32 and, adjacently to the plate 32 or on its upper side and lower side, axial stators 32 which each have stationary bearing surfaces 35. The plate 32 comprises rotating bearing surfaces 36 which lie opposite the stationary bearing surface 35. Between the axial gas bearing 31 and impeller 16, a channel 41, which are connected to the compression side of the cooling system 1, leads below the impeller 16. The pressurised coolant is guided below the impeller 16 by this channel 41 in a gaseous state in order to protect the axial gas bearing 31 from the ingress of particles.

[0026] Preferably, the rotating bearing surfaces 25 of the radial gas bearing 22 and/or the rotating bearing surfaces 36 of the axial gas laser 31 have surfaces which comprise grooves. Fishbone patterns are preferably provided. Such grooves or surface indentations are preferably introduced using an ultra-short pulse laser, in particular picosecond laser. This enables a processing with very short processing times. Moreover, this processing step does not require reworking and meets the high demands of the precise design. The very short laser impulses in the microsecond range lead to a direct sublimation of the material. Thus, a production of these grooves can be provided which does not require reworking, in particular is free from burrs. In particular, an ion beam method is used. Alternatively, a micro-machining can also be provided.

[0027] In an installation situation, the radial blower 11 is aligned vertically in the cooling system 1. Here, the compressor 27 is aligned downwards, and the engine housing 21 is aligned vertically upwards. The radial blower 11 can advantageously be arranged directly above a flooded evaporator 66, such that, where necessary, condensate emerging when the cooling system 1 is at a standstill flows downwards back into the evaporator 66.

[0028] In FIG. 2, a schematically enlarged view of the axial gas bearing 31 and a connection of the compressor 27 to the engine housing 21 of the radial blower 11 is depicted. The connection of the compressor 27 with its housing 52 to the engine housing 21 of the radial blower 11 is carried out without using a labyrinth sealing or similar. The supply of the pressurised coolant via the channel 41 is used to prevent an ingress of particles into the axial gas bearing 31. The axial gas bearing 31 itself has such a narrow gap between the bearing surfaces 35 of the stator 34 and the bearing surfaces 36 of the rotating plate 32 that a seal between a rotor chamber 46 in the housing 21 and a gas chamber 49 in the compressor 27 is formed by the axial gas bearing 31 itself. Seen in the radial direction, the rotor chamber 46 is formed between a through-hole 47 in the engine housing 21 and the shaft 17 mounted therein. The gas chamber 49 is formed between a housing portion 51 of the engine housing 21 or housing 52 of the compressor 27 and the impeller 16. A housing 52 of the compressor 27 preferably engages around the housing portion 51 and is fixedly connected to the engine housing 21 outside of this housing portion 51.

[0029] A pressure port 54 for the pressurised coolant is provided on the engine housing 21, which is supplied to the channel 41. In a region in which the rotor chamber 46 and the gas chamber 49 are adjacent to each other, the coolant flows mainly in the direction of the gas chamber 49; the gas flow is held off through the axial bearing 31 in the counter-direction, which seals the rotor chamber 46.

[0030] A seal between a pressure side of the compressor 27 and the engine housing 21 is carried out as a result of this arrangement. The compressor 27 is preferably formed as a multi-step compressor or turbo compressor. A first step forms the impeller 26, and the second step forms the impeller 16. In particular, the seal between the pressure side of the second step or the impeller 16 of the compressor 27 and the engine housing 21 of the radial blower 11 can be carried out. In this way, a lower pressure can be set in the engine housing than on the pressure side of the compressor 27, whereby a condensation of the coolant in the radial bearings 22, 23 is prevented. Furthermore, the pressure port 54 can preferably have a filter element. This serves to prevent any particles reaching the compressor 27 and/or the axial gas bearing 31.

[0031] This radial blower 11 can furthermore have a heating device 56 in the region of the axial gas bearing 31 or adjacent to an axial stator 34 or between the two axial stators 34. Such a heating device 56 serves to heat the axial gas bearing 31 to a temperature which is above the dew point of the coolant at an acting pressure. Thus, a condensation of the coolant can be prevented. Such a heating device 56 can be formed as an electrically driven heater, such as by a resistance heating element or a PTC element, for example.

[0032] A vibrometer 61 is preferably provided between the engine 20 and the lower radial gas bearing 22, said vibrometer being allocated to the shaft 17. This vibrometer 61 is a measuring device for quantifying mechanical vibrations. Such a vibrometer 61 can be used to measure vibration frequency and vibration amplitude. For example, a so-called laser Doppler vibrometer can be used. This vibrometer 61 is inserted into a housing opening 62 of the engine housing 21 and preferably arranged in a pressure-tight manner. This can be carried out by means of an O-ring seal 63, for example. Thus, the pressure in the rotor chamber 46 can be maintained for the hydrodynamic operation of the radial and axial gas bearings 22, 23, 31. A measuring surface of the vibrometer 61 is aligned tangentially to the peripheral surface of the shaft 17. Here, the measuring surface can advantageously lie on a bearing sleeve surrounding a radial gas bearing 22, 23. During the operation of the radial blower 11, the frequency and amplitude can be permanently detected by the vibrometer 61 and forwarded to a controller 71 of the radial blower or the cooling system. Thus, the current operating point or the operating points prevailing during cooling of the radial blower 11 can be ascertained. In addition, a comparison with a threshold value can be performed at the same time. Such a threshold value can be a critical operating state in which damage to the bearing(s) or further components of the radial blower is to be expected. In particular to the effect that there is blocking of the shaft 17 in the engine housing 21 or the impellers 16, 16 in the compressor 27.

[0033] Alternatively, a vibrometer 61 can additionally be provided between the engine 20 and the upper radial gas bearing 23.

[0034] A further vibrometer 64 can be provided for an additional monitoring of operating states of the radial blower 11, said vibrometer being positioned on the rotational axis of the shaft 17 and pointing onto an end-face end of the shaft 17 in relation to a measuring surface. Thus, eccentricities during the rotating drive of the shaft 17 can also be conceptively evaluated.

[0035] Analogously to the vibrometer 61, this additional vibrometer 64 is in turn positioned in a housing cover 65 in a medium-tight manner.

[0036] In FIG. 3, a schematic view of a cooling system 1 is depicted. This cooling system 1 is only exemplary and functions according to the principle of evaporation chill in particular. A coolant is in an evaporator 66. The necessary energy or heat to evaporate the coolant is drawn from the surroundings. The coolant receives this energy and converts into a gaseous state. In the gaseous state, the coolant is supplied to one or, according to the exemplary embodiment, several radial blowers 11 via a line 67, said radial rans each having a compressor 27. The coolant is compressed to a high pressure and a high temperature, which is respectively higher than the starting pressure and the starting temperature before the compressor 11. Then the coolant is supplied to a condenser or a capacitor 68. The coolant is condensed in this condenser by cooling. Then the coolant with high pressure is led through a throttle member, in particular an expansion valve 69. The coolant expands or is transferred to lower pressure and can be supplied to the evaporator 66 in the liquid state in order to in turn remove the heat from the surroundings. The cooling system 1 is a closed cooling circuit.

[0037] A controller 71 of the cooling system 1 is provided to control the individual radial blower 11, by means of which controller the individual radial blowers 11 can be controlled. Preferably, the radial blowers 11 are each connected to the controller 71 by a bus system 72. The compressor controller or a radial blower controller preferably functions according to the master-slave principle. The master function is allocated to one of the radial blowers 11. The further radial blowers 11 are operated as a duster as so-called slaves. The controller 71 detects the measurements of the sensors of the radial blower by the master. Based on these detected or present measurements, the further radial blowers are respectively switched on, such that the duster of the radial blowers 11 is operated in a regulated energy minimum. Here, a protective function of each individual radial blower 11 is maintained.

[0038] In order to obtain a safe operating range of the radial blower 11 in the cooling system 1, control-technical or regulatory algorithms are used in the controller 71 for controlling the radial blower 11 in such a way that no critical operating point can emerge for the respective radial blower 11. Furthermore, the radial blowers 11 can also communicate with one another via the bus system 72, in order to autonomously obtain the control for achieving an energy efficiency maximum based on the measurements present in the radial blower 11 itself, in particular based on the measurements present in the master radial blower 11.