CA2932783A1 - Compressor system for a rail vehicle and method for operating the compressor system with safe emergency operation - Google Patents
Compressor system for a rail vehicle and method for operating the compressor system with safe emergency operation Download PDFInfo
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- CA2932783A1 CA2932783A1 CA2932783A CA2932783A CA2932783A1 CA 2932783 A1 CA2932783 A1 CA 2932783A1 CA 2932783 A CA2932783 A CA 2932783A CA 2932783 A CA2932783 A CA 2932783A CA 2932783 A1 CA2932783 A1 CA 2932783A1
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- pressure
- compressor
- rotational speed
- electric machine
- compressed
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- 238000000034 method Methods 0.000 title claims abstract description 12
- 238000012544 monitoring process Methods 0.000 claims abstract description 5
- 230000033228 biological regulation Effects 0.000 claims description 31
- 230000009849 deactivation Effects 0.000 claims description 16
- 230000001105 regulatory effect Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 230000004913 activation Effects 0.000 description 3
- 238000001994 activation Methods 0.000 description 3
- 238000001816 cooling Methods 0.000 description 3
- 230000001419 dependent effect Effects 0.000 description 3
- 238000010276 construction Methods 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 208000036366 Sensation of pressure Diseases 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000010348 incorporation Methods 0.000 description 1
- 238000007726 management method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 229920000136 polysorbate Polymers 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/08—Regulating by delivery pressure
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61D—BODY DETAILS OR KINDS OF RAILWAY VEHICLES
- B61D27/00—Heating, cooling, ventilating, or air-conditioning
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61L—GUIDING RAILWAY TRAFFIC; ENSURING THE SAFETY OF RAILWAY TRAFFIC
- B61L25/00—Recording or indicating positions or identities of vehicles or trains or setting of track apparatus
- B61L25/02—Indicating or recording positions or identities of vehicles or trains
- B61L25/021—Measuring and recording of train speed
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61L—GUIDING RAILWAY TRAFFIC; ENSURING THE SAFETY OF RAILWAY TRAFFIC
- B61L25/00—Recording or indicating positions or identities of vehicles or trains or setting of track apparatus
- B61L25/02—Indicating or recording positions or identities of vehicles or trains
- B61L25/025—Absolute localisation, e.g. providing geodetic coordinates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B41/00—Pumping installations or systems specially adapted for elastic fluids
- F04B41/02—Pumping installations or systems specially adapted for elastic fluids having reservoirs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/06—Control using electricity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/20—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by changing the driving speed
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61L—GUIDING RAILWAY TRAFFIC; ENSURING THE SAFETY OF RAILWAY TRAFFIC
- B61L2205/00—Communication or navigation systems for railway traffic
- B61L2205/04—Satellite based navigation systems, e.g. global positioning system [GPS]
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2203/00—Motor parameters
- F04B2203/02—Motor parameters of rotating electric motors
- F04B2203/0209—Rotational speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2205/00—Fluid parameters
- F04B2205/05—Pressure after the pump outlet
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
The invention relates to a compressor system for a rail vehicle, comprising a compressor (3), driven by an electrical machine (1) via a drive shaft (2), for producing compressed air for at least one compressed air tank (4), wherein the electrical machine (1) can be activated at least indirectly via a control device (5) for operating the electrical machine (1) at at least one nominal speed (n) between a maximum speed (m) and a minimum speed (i), wherein furthermore at least one pressure sensor (7) for determining the pressure for the control device (5) is disposed in a compressed-air-carrying line (6) downstream of the compressor (3). According to the invention, a final control element (8) for continuously influencing the speed of the electrical machine (1) is disposed between an electrical supply (15) and the electrical machine (1), wherein the final control element (8) can be activated via the control device (5), and wherein a pressure switch (16) for monitoring the pressure in the at least one compressed air tank (4) and for influencing at least the speed of the electrical machine (1) is disposed in the compressed-air-carrying line (6) downstream of the compressor (3). Furthermore, the invention also relates to a method for controlling the compressor system according to the invention, wherein the compressor (3) is operated at a variable speed, assuming any intermediate value between the maximum speed (m) and the minimum speed (i), and wherein the pressure switch (16) monitors the pressure in the at least one compressed air tank (4) and has an indirect influence at least on the speed of the electrical machine (1).
Description
Compressor system for a rail vehicle and method for operating the compressor sys-tem with safe emergency operation FIELD OF THE INVENTION
The invention relates to a compressor system for a rail vehicle, comprising a compressor which is driven by an electric machine via a drive shaft and which serves for generating compressed air for at least one compressed-air vessel, wherein the electric machine can be controlled at least indirectly by means of a regulation device for operation of the elec-tric machine at at least a rated rotational speed between a maximum rotational speed and a minimum rotational speed, wherein furthermore, in a compressed air-conducting line arranged downstream of the compressor, there is arranged at least one pressure sensor '
The invention relates to a compressor system for a rail vehicle, comprising a compressor which is driven by an electric machine via a drive shaft and which serves for generating compressed air for at least one compressed-air vessel, wherein the electric machine can be controlled at least indirectly by means of a regulation device for operation of the elec-tric machine at at least a rated rotational speed between a maximum rotational speed and a minimum rotational speed, wherein furthermore, in a compressed air-conducting line arranged downstream of the compressor, there is arranged at least one pressure sensor '
- 2 -for determining the pressure for the regulation device. The invention also relates to a method for controlling the compressor system according to the invention.
BACKGROUND TO THE INVENTION
Compressors in rail vehicles are subject to a variety of, in part, conflicting demands, such as for example a high delivery output, adequate activation duration, low sound emissions, low energy consumption, a small structural space, and low purchase and life-cycle costs. Here, the compressor must satisfy extremely different demand profiles de-pending on the operating state of the rail vehicle. The typical problem in designing a compressor is that of finding the best comprise between these demands which is ac-ceptable in all operating states of the rail vehicle. In general, electrically driven com-pressors are used in rail vehicles. The operation of the compressors takes the form of on/off operation with a constant rotational speed, the so-called rated rotational speed, between the lower activation pressure and the upper deactivation pressure. The compres-sor is dimensioned such that a predefined filling time is attained and a minimum activa-tion duration during operation is not undershot.
From the generally known prior art, it emerges that, between the different operating states of the rail vehicle, there is no difference in the operation of the compressor. Here, the fan of the cooling system is subject to the same operating regime as the compressor, as the fan is generally directly jointly driven by the compressor.
It is also known that a more complex construction and more complex operation of the compressor system in relation to regular operation and in relation to the regular con-struction necessitate additional, in particular electronic components which may exhibit additional probability of failure or at least additional susceptibility to failure. In other ,
BACKGROUND TO THE INVENTION
Compressors in rail vehicles are subject to a variety of, in part, conflicting demands, such as for example a high delivery output, adequate activation duration, low sound emissions, low energy consumption, a small structural space, and low purchase and life-cycle costs. Here, the compressor must satisfy extremely different demand profiles de-pending on the operating state of the rail vehicle. The typical problem in designing a compressor is that of finding the best comprise between these demands which is ac-ceptable in all operating states of the rail vehicle. In general, electrically driven com-pressors are used in rail vehicles. The operation of the compressors takes the form of on/off operation with a constant rotational speed, the so-called rated rotational speed, between the lower activation pressure and the upper deactivation pressure. The compres-sor is dimensioned such that a predefined filling time is attained and a minimum activa-tion duration during operation is not undershot.
From the generally known prior art, it emerges that, between the different operating states of the rail vehicle, there is no difference in the operation of the compressor. Here, the fan of the cooling system is subject to the same operating regime as the compressor, as the fan is generally directly jointly driven by the compressor.
It is also known that a more complex construction and more complex operation of the compressor system in relation to regular operation and in relation to the regular con-struction necessitate additional, in particular electronic components which may exhibit additional probability of failure or at least additional susceptibility to failure. In other ,
- 3 -words, the incorporation of additional electronics components in the compressor system also introduces into the compressor system the additional probability of failure of the individual electronics components. The probability of faults and the risk of failure of the compressor system are thus increased. Since the compressor system supplies compressed air to the brake system, a failure of the compressor system generally has the effect of bringing the rail vehicle to a standstill.
DISCLOSURE OF THE INVENTION
It is therefore the object of the present invention to optimize a compressor system and a method for operating the compressor system such that more energy-efficient operation of the compressor system, with a reduction in sound emissions, is possible without an increase in the probability of faults and risk of failure of the compressor system.
With regard to a device, the object is achieved, proceeding from a compressor system as per the preamble of Claim 1, in conjunction with the characterizing features of said claim. With regard to a method, the object is achieved as per Claim 6 in conjunction with the characterizing features thereof. Advantageous refinements of the invention emerge from the following dependent claims.
According to the invention, an actuator for the continuous manipulation of the rotational speed of the electric machine is arranged between an electrical supply and the electric machine, wherein the actuator can be controlled by way of the regulation device, and wherein, in the compressed air-conducting line arranged downstream of the compressor, there is arranged a pressure switch for monitoring of the pressure in the at least one compressed-air vessel and for manipulation of at least the rotational speed of the electric machine.
DISCLOSURE OF THE INVENTION
It is therefore the object of the present invention to optimize a compressor system and a method for operating the compressor system such that more energy-efficient operation of the compressor system, with a reduction in sound emissions, is possible without an increase in the probability of faults and risk of failure of the compressor system.
With regard to a device, the object is achieved, proceeding from a compressor system as per the preamble of Claim 1, in conjunction with the characterizing features of said claim. With regard to a method, the object is achieved as per Claim 6 in conjunction with the characterizing features thereof. Advantageous refinements of the invention emerge from the following dependent claims.
According to the invention, an actuator for the continuous manipulation of the rotational speed of the electric machine is arranged between an electrical supply and the electric machine, wherein the actuator can be controlled by way of the regulation device, and wherein, in the compressed air-conducting line arranged downstream of the compressor, there is arranged a pressure switch for monitoring of the pressure in the at least one compressed-air vessel and for manipulation of at least the rotational speed of the electric machine.
- 4 -In other words, the actuator is situated upstream of the electric machine in the power flow, and is thus positioned ahead of the electric machine. The actuator permits opera-tion of the electric machine at different rotational speeds. Frequency converters or in-verters are particularly suitable for this purpose. In a manner dependent on frequency, the rotational speed of the electric machine and thus the operation of the compressor are adapted. However, the additional electronic components for regulating the rotational speed, in particular the additional sensors, cables and the actuator, give rise to an in-crease in the probability of faults and risk of failure of the compressor system.
By means of the pressure switch for monitoring the pressure in the at least one com-pressed-air vessel, the reliability of a compressor system of said type is increased, and the possibility of reliable emergency running operation is realized.
Specifically, in the event of a drop in pressure, the pressure switch can indirectly manipulate at least the rotational speed of the electric machine. By means of a signal from the pressure switch to the effect that a certain lower pressure in the at least one compressed-air vessel has been undershot, the compressor can be activated, and in particular the rotational speed of the compressor can be increased, in order to increase the pressure in the at least one compressed-air vessel up to a certain upper pressure. Thus, the pressure switch manipu-lates at least the rotational speed of the compressor only when the pressure reaches ei-ther the minimum pressure or the upper deactivation pressure. When the minimum pres-sure is reached, the rotational speed is increased, wherein, when the upper deactivation pressure is reached, it is at least the case that the rotational speed is reduced, or the com-pressor is deactivated. In other words, in the event of a fault in the compressor system which leads to the minimum pressure in the at least one compressed-air vessel being reached, regular operation of the compressor is resumed such that the compressor is op-erated at rated rotational speed.
,
By means of the pressure switch for monitoring the pressure in the at least one com-pressed-air vessel, the reliability of a compressor system of said type is increased, and the possibility of reliable emergency running operation is realized.
Specifically, in the event of a drop in pressure, the pressure switch can indirectly manipulate at least the rotational speed of the electric machine. By means of a signal from the pressure switch to the effect that a certain lower pressure in the at least one compressed-air vessel has been undershot, the compressor can be activated, and in particular the rotational speed of the compressor can be increased, in order to increase the pressure in the at least one compressed-air vessel up to a certain upper pressure. Thus, the pressure switch manipu-lates at least the rotational speed of the compressor only when the pressure reaches ei-ther the minimum pressure or the upper deactivation pressure. When the minimum pres-sure is reached, the rotational speed is increased, wherein, when the upper deactivation pressure is reached, it is at least the case that the rotational speed is reduced, or the com-pressor is deactivated. In other words, in the event of a fault in the compressor system which leads to the minimum pressure in the at least one compressed-air vessel being reached, regular operation of the compressor is resumed such that the compressor is op-erated at rated rotational speed.
,
- 5 -In a preferred exemplary embodiment, the pressure switch is operatively connected to the regulation device for the purposes of indirect manipulation of the rotational speed of the electric machine. In other words, the pressure switch transmits the generated signals to the regulation device, wherein the latter, preferably by way of an integrated control algorithm, adapts the rotational speed of the electric machine to the received signal.
In a further preferred exemplary embodiment, an isolating switch for separating the reg-ulation device and the actuator from the electric machine is connected downstream of the actuator. In this case, the isolating switch is in particular arranged between the elec-trical supply and the electric machine, and thus constitutes a bridge both between the actuator and the electric machine and between the electrical supply and the electric ma-chine.
Furthermore, the pressure switch is preferably connected to the isolating switch via an interposed control logic unit. The isolating switch is consequently independent of the regulation device and can be operated by way of the control logic unit, which receives signals from the pressure switch.
It is preferably provided that the regulation device at least indirectly controls a cooler unit which is arranged downstream of the compressor and which has a cooler fan, wherein a rotational speed of the cooler fan can be continuously adjusted by the regula-tion device. For this purpose, an actuator is preferably integrated in the cooler unit. It is alternatively also conceivable for the actuator to be at least positioned upstream of the cooler unit. It is likewise conceivable for an actuator to have two control outputs, such that both the electric machine and the cooler fan are controlled by way of a common actuator.
In a further preferred exemplary embodiment, an isolating switch for separating the reg-ulation device and the actuator from the electric machine is connected downstream of the actuator. In this case, the isolating switch is in particular arranged between the elec-trical supply and the electric machine, and thus constitutes a bridge both between the actuator and the electric machine and between the electrical supply and the electric ma-chine.
Furthermore, the pressure switch is preferably connected to the isolating switch via an interposed control logic unit. The isolating switch is consequently independent of the regulation device and can be operated by way of the control logic unit, which receives signals from the pressure switch.
It is preferably provided that the regulation device at least indirectly controls a cooler unit which is arranged downstream of the compressor and which has a cooler fan, wherein a rotational speed of the cooler fan can be continuously adjusted by the regula-tion device. For this purpose, an actuator is preferably integrated in the cooler unit. It is alternatively also conceivable for the actuator to be at least positioned upstream of the cooler unit. It is likewise conceivable for an actuator to have two control outputs, such that both the electric machine and the cooler fan are controlled by way of a common actuator.
- 6 -With regard to the method, the compressor is operated with a variable rotational speed which assumes any intermediate value between the maximum rotational speed and the minimum rotational speed, wherein the pressure switch monitors the pressure in the at least one compressed-air vessel and indirectly manipulates at least the rotational speed of the electric machine. By virtue of the fact that the cooling unit is not connected either directly or indirectly to the compressor, separate control of the cooling unit and thus separate adjustment of the rotational speed of the cooler fan are performed.
It is advan-tageously also possible for the compressor and the cooler fan to be deactivated.
In a further exemplary embodiment, when the minimum pressure in the at least one compressed-air vessel is reached, the regulation device receives from the pressure switch a signal for triggering the actuator to operate the compressor at at least the rated rota-tional speed until the deactivation pressure is reached. In this way, it is possible in par-ticular to counteract faulty sensors and/or cables. Specifically, the regulation device con-trols the actuator in accordance with the output of the pressure switch.
In a further exemplary embodiment, when the minimum pressure in the at least one compressed-air vessel is reached, the control logic unit receives from the pressure switch a signal for triggering the isolating switch and separating the regulation device and the actuator from the electric machine, wherein the compressor is operated, via the isolating switch, with the rated rotational speed until the deactivation pressure is reached. De-pending on the position of the isolating switch, it is also possible to generate a rotational speed higher than the rated rotational speed for the electric machine. For this purpose, the isolating switch connects the electric machine directly to the electrical supply.
Therefore, the regulation device cannot have any influence on the electric machine and thus on the rotational speed of the compressor. In this way, it is possible in particular for
It is advan-tageously also possible for the compressor and the cooler fan to be deactivated.
In a further exemplary embodiment, when the minimum pressure in the at least one compressed-air vessel is reached, the regulation device receives from the pressure switch a signal for triggering the actuator to operate the compressor at at least the rated rota-tional speed until the deactivation pressure is reached. In this way, it is possible in par-ticular to counteract faulty sensors and/or cables. Specifically, the regulation device con-trols the actuator in accordance with the output of the pressure switch.
In a further exemplary embodiment, when the minimum pressure in the at least one compressed-air vessel is reached, the control logic unit receives from the pressure switch a signal for triggering the isolating switch and separating the regulation device and the actuator from the electric machine, wherein the compressor is operated, via the isolating switch, with the rated rotational speed until the deactivation pressure is reached. De-pending on the position of the isolating switch, it is also possible to generate a rotational speed higher than the rated rotational speed for the electric machine. For this purpose, the isolating switch connects the electric machine directly to the electrical supply.
Therefore, the regulation device cannot have any influence on the electric machine and thus on the rotational speed of the compressor. In this way, it is possible in particular for
- 7 -a failure or a fault of the regulation device as a whole, together with all associated sen-sors and the actuator, to be counteracted.
It is particularly preferably provided that, after the pressure of the at least one corn-pressed-air vessel has fallen to the minimum pressure at least twice, the electric machine is operated with intermittent alternation between at least the rated rotational speed when the pressure falls to the minimum pressure and deactivation of the compressor when the deactivation pressure is reached. In other words, the rotational speed of the electric ma-chine and thus the rotational speed of the compressor are varied no further, in order to maintain a relatively constant pressure in the at least one compressed-air vessel. It is however also conceivable for the compressor to be operated not with the rated rotational speed but with a maximum rotational speed in order to permit faster filling of the at least one compressed-air vessel.
BRIEF DESCRIPTION OF THE DRAWINGS
Further measures which improve the invention will be presented in more detail below in conjunction with the description of preferred exemplary embodiments of the invention and with reference to the figures, in which:
figure 1 shows a block circuit diagram of the compressor system according to the invention, figure 2 shows a block circuit diagram of the compressor system according to the invention as per a second exemplary embodiment, and ' ,
It is particularly preferably provided that, after the pressure of the at least one corn-pressed-air vessel has fallen to the minimum pressure at least twice, the electric machine is operated with intermittent alternation between at least the rated rotational speed when the pressure falls to the minimum pressure and deactivation of the compressor when the deactivation pressure is reached. In other words, the rotational speed of the electric ma-chine and thus the rotational speed of the compressor are varied no further, in order to maintain a relatively constant pressure in the at least one compressed-air vessel. It is however also conceivable for the compressor to be operated not with the rated rotational speed but with a maximum rotational speed in order to permit faster filling of the at least one compressed-air vessel.
BRIEF DESCRIPTION OF THE DRAWINGS
Further measures which improve the invention will be presented in more detail below in conjunction with the description of preferred exemplary embodiments of the invention and with reference to the figures, in which:
figure 1 shows a block circuit diagram of the compressor system according to the invention, figure 2 shows a block circuit diagram of the compressor system according to the invention as per a second exemplary embodiment, and ' ,
- 8 -figure 3 shows two related diagrams, wherein a rotational speed of the compressor is plotted versus time in the upper diagram, and a pressure of the compressor is plotted versus time in the lower diagram.
DETAILED DESCRIPTION OF A PREFERRED EMBODIMENT
As per figure 1, a compressor system for a rail vehicle has an electric machine 1 which, via a drive shaft 2, drives a compressor 3 for generating compressed air. The compressed air generated by the compressor 3 is conducted via a compressed air-conducting line 6 to a cooler unit 9 which has a cooler fan 14. A pressure sensor 7 and a temperature sensor 13b are arranged downstream of the cooler unit 9 in the compressed air-conducting line 6. Furthermore, the compressed air-conducting line 6 issues into a pre-separator 11, downstream of which there is connected an air treatment system 12. The dried com-pressed air, which has been purified of particles, is then fed into a compressed-air vessel 4. Furthermore, in the compressed-air conducting line 6, there is arranged a pressure switch 16 for the monitoring of the pressure in the compressed-air vessel 4 and for the indirect manipulation of the rotational speed of the electric machine 1 and of the cooler fan 14.
A temperature sensor 13a, which is arranged at the compressor 3, and the temperature sensor 13b and the pressure sensor 7 all transmit the measured temperatures and the measured pressure to the regulation device 5. Furthermore, via a signal input 10, the regulation device 5 also receives signals from other sensors ¨ not illustrated here ¨ or from a train management system. Furthermore, the regulation device 5 is suitable for both controlling the rotational speed of the cooler unit 9 and transmitting signals to an actuator 8. The actuator 8, which is in the form of a frequency converter, sets the rota-tional speed of the electric machine 1 and thus the rotational speed of the compressor 3.
'
DETAILED DESCRIPTION OF A PREFERRED EMBODIMENT
As per figure 1, a compressor system for a rail vehicle has an electric machine 1 which, via a drive shaft 2, drives a compressor 3 for generating compressed air. The compressed air generated by the compressor 3 is conducted via a compressed air-conducting line 6 to a cooler unit 9 which has a cooler fan 14. A pressure sensor 7 and a temperature sensor 13b are arranged downstream of the cooler unit 9 in the compressed air-conducting line 6. Furthermore, the compressed air-conducting line 6 issues into a pre-separator 11, downstream of which there is connected an air treatment system 12. The dried com-pressed air, which has been purified of particles, is then fed into a compressed-air vessel 4. Furthermore, in the compressed-air conducting line 6, there is arranged a pressure switch 16 for the monitoring of the pressure in the compressed-air vessel 4 and for the indirect manipulation of the rotational speed of the electric machine 1 and of the cooler fan 14.
A temperature sensor 13a, which is arranged at the compressor 3, and the temperature sensor 13b and the pressure sensor 7 all transmit the measured temperatures and the measured pressure to the regulation device 5. Furthermore, via a signal input 10, the regulation device 5 also receives signals from other sensors ¨ not illustrated here ¨ or from a train management system. Furthermore, the regulation device 5 is suitable for both controlling the rotational speed of the cooler unit 9 and transmitting signals to an actuator 8. The actuator 8, which is in the form of a frequency converter, sets the rota-tional speed of the electric machine 1 and thus the rotational speed of the compressor 3.
'
- 9 -Furthermore, the actuator 8 has two outlets and thus also sets the rotational speed of the cooler fan 14 by way of the regulation device 5. In this case, the actuator 8 is, for the continuous manipulation of the rotational speed of the electric machine 1, arranged be-tween an electrical supply 15 and the electric machine 1. In this case, when a minimum pressure e in the compressed-air vessel 4 is reached, the regulation device 5 receives from the pressure switch 16 a signal for triggering the actuator 8 to operate the compres-sor 3 at the rated rotational speed n until a deactivation pressure d is reached.
In Figure 2, an isolating switch 17 for separating the regulation device 5 and the actuator 8 from the electric machine 1 is connected downstream of the actuator 8. The pressure switch 16 is connected to the isolating switch 17 via an interposed control logic unit 18.
In this case, when a minimum pressure e in the compressed-air vessel 4 is reached, the control logic unit 18 receives from the pressure switch 16 a signal for triggering the iso-lating switch 17 and separating the regulation device 5 and the actuator 8 from the elec-tric machine 1. The compressor 3 is then operated, via the isolating switch 17, at the rated rotational speed n until a deactivation pressure d is reached.
Figure 3 graphically illustrates the above-described process in the event of a pressure drop in the compressed-air vessel 4 being measured by way of the pressure switch 16. In a region a, the compressor 3 is operated at a rotational speed between a minimum rota-tional speed i and the rated rotational speed n, wherein the pressure in the compressed-air vessel 4 is kept in a certain range. Thus, in the region a, the compressor 3 is in regu-lated operation. The rotational speed is variable and dependent on the situation.
In a region b, the pressure in the compressed-air vessel 4 and the rotational speed of the compressor 3 spontaneously drop. In other words, in the region b, a fault has occurred during regulated operation, which fault has led to a measured pressure drop.
'
In Figure 2, an isolating switch 17 for separating the regulation device 5 and the actuator 8 from the electric machine 1 is connected downstream of the actuator 8. The pressure switch 16 is connected to the isolating switch 17 via an interposed control logic unit 18.
In this case, when a minimum pressure e in the compressed-air vessel 4 is reached, the control logic unit 18 receives from the pressure switch 16 a signal for triggering the iso-lating switch 17 and separating the regulation device 5 and the actuator 8 from the elec-tric machine 1. The compressor 3 is then operated, via the isolating switch 17, at the rated rotational speed n until a deactivation pressure d is reached.
Figure 3 graphically illustrates the above-described process in the event of a pressure drop in the compressed-air vessel 4 being measured by way of the pressure switch 16. In a region a, the compressor 3 is operated at a rotational speed between a minimum rota-tional speed i and the rated rotational speed n, wherein the pressure in the compressed-air vessel 4 is kept in a certain range. Thus, in the region a, the compressor 3 is in regu-lated operation. The rotational speed is variable and dependent on the situation.
In a region b, the pressure in the compressed-air vessel 4 and the rotational speed of the compressor 3 spontaneously drop. In other words, in the region b, a fault has occurred during regulated operation, which fault has led to a measured pressure drop.
'
- 10 -When the pressure in the compressed-air vessel 4 reaches the minimum pressure e, the pressure switch 16 reacts and, in a region c, increases the rotational speed of the electric machine 1 and thus the rotational speed of the compressor 3 to the rated rotational speed n indirectly, either via the isolating switch 17 or via the actuator 8.
Consequently, in the region c, the reaction of the pressure switch 16 occurs for the switchover of operation from regulated operation to non-regulated operation. There are two states of non-regulated operation. These are firstly the operation of the compressor 3 at the rated rota-tional speed n, and secondly the deactivation of the compressor 3. The cooler fan 14 (not illustrated here) is also operated analogously to the operation of the compressor 3.
After a deactivation pressure d has been reached in the compressed-air vessel 4, the compressor 3 is deactivated and is operated once again at a rotational speed between the minimum rotational speed i and the rated rotational speed n, such that the pressure in the compressed-air vessel 4 is kept in a certain range.
The invention is not restricted to the preferred exemplary embodiments described above.
Rather, modifications thereto are also possible which are also encompassed by the scope of protection of the following claims. For example, it is also possible for the compressor 3 to provide a feed to a multiplicity of compressed-air vessels 4. It may also be provided that, when the minimum pressure e in the compressed-air vessel 4 is reached, the rota-tional speed of the electric machine 1 and thus the rotational speed of the compressor 3 are increased to a maximum rotational speed m rather than just the rated rotational speed n.
=
Consequently, in the region c, the reaction of the pressure switch 16 occurs for the switchover of operation from regulated operation to non-regulated operation. There are two states of non-regulated operation. These are firstly the operation of the compressor 3 at the rated rota-tional speed n, and secondly the deactivation of the compressor 3. The cooler fan 14 (not illustrated here) is also operated analogously to the operation of the compressor 3.
After a deactivation pressure d has been reached in the compressed-air vessel 4, the compressor 3 is deactivated and is operated once again at a rotational speed between the minimum rotational speed i and the rated rotational speed n, such that the pressure in the compressed-air vessel 4 is kept in a certain range.
The invention is not restricted to the preferred exemplary embodiments described above.
Rather, modifications thereto are also possible which are also encompassed by the scope of protection of the following claims. For example, it is also possible for the compressor 3 to provide a feed to a multiplicity of compressed-air vessels 4. It may also be provided that, when the minimum pressure e in the compressed-air vessel 4 is reached, the rota-tional speed of the electric machine 1 and thus the rotational speed of the compressor 3 are increased to a maximum rotational speed m rather than just the rated rotational speed n.
=
- 11 -List of reference signs 1 Electric machine 2 Drive shaft 3 Compressor 4 Compressed-air vessel 5 Regulation device 6 Compressed air-conducting line 7 Pressure sensor 8 Actuator 9 Cooler unit 10 Signal input 11 Pre-separator
12 Air treatment system 13a, 13b Temperature sensor 14 Cooler fan 15 Electrical supply 16 Pressure switch 17 Isolating switch 18 Control logic unit a, b, c Region d Deactivation pressure e Minimum pressure i Minimum rotational speed m Maximum rotational speed n Rated rotational speed
Claims (9)
1. Compressor system for a rail vehicle, comprising a compressor (3) which is driv-en by an electric machine (1) via a drive shaft (2) and which serves for generating com-pressed air for at least one compressed-air vessel (4), wherein the electric machine (1) can be controlled at least indirectly by means of a regulation device (5) for operation of the electric machine (1) at at least a rated rotational speed (n) between a maximum rota-tional speed (m) and a minimum rotational speed (i), wherein furthermore, in a com-pressed air-conducting line (6) arranged downstream of the compressor (3), there is ar-ranged at least one pressure sensor (7) for determining the pressure for the regulation device (5), characterized in that an actuator (8) for the continuous manipulation of the rotational speed of the electric machine (1) is arranged between an electrical supply (15) and the electric machine (1), wherein the actuator (8) can be controlled by way of the regulation device (5), and wherein, in the compressed air-conducting line (6) arranged downstream of the compressor (3), there is arranged a pressure switch (16) for monitoring of the pressure in the at least one compressed-air vessel (4) and for manipulation of at least the rotational speed of the electric machine (1).
2. Compressor system according to Claim 1, characterized in that the pressure switch (16) is operatively connected to the regulation device (5) for the purposes of indirect manipulation of the rotational speed of the electric machine (1).
3. Compressor system according to Claim 1, characterized in that an isolating switch (17) for separating the regulation device (5) and the actuator (8) from the electric machine (1) is connected downstream of the actua-tor (8).
4. Compressor system according to Claim 3, characterized in that the pressure switch (16) is connected to the isolating switch (17) via an interposed control logic unit (18).
5. Compressor system according to Claim 1, characterized in that the regulation device (5) at least indirectly controls a cooler unit (9) which is arranged downstream of the compressor (3) and which has a cooler fan (14), wherein a rotational speed of the cooler fan (14) can be continuously adjusted by the regulation device (5).
6. Method for controlling a compressor system according to one of Claims 1 to 5, characterized in that the compressor (3) is operated with a variable rotational speed which assumes any intermediate value between the maximum rotational speed (m) and the minimum rotational speed (i), wherein the pressure switch (16) monitors the pressure in the at least one compressed-air vessel (4) and indirectly manipulates at least the rota-tional speed of the electric machine (1).
7. Method according to Claim 6, characterized in that, when the minimum pressure (e) in the at least one compressed-air vessel (4) is reached, the control logic unit (18) receives from the pressure switch (16) a signal for triggering the isolating switch (17) and separating the regulation device (5) and the actuator (8) from the electric machine (1), wherein the compressor (3) is op-erated, via the isolating switch (17), with the rated rotational speed (n) until the deactiva-tion pressure (d) is reached.
8. Method according to Claim 6, characterized in that, when the minimum pressure (e) in the at least one compressed-air vessel (4) is reached, the regulation device (5) receives from the pressure switch (16) a signal for triggering the actuator (8) to operate the compressor (3) at at least the rated rotational speed (n) until the deactivation pressure (d) is reached.
9. Method according to one of Claims 6 to 8, characterized in that, after the pressure of the at least one compressed-air vessel (4) has fallen to the minimum pressure (e) at least twice, the electric machine (1) is operated with intermittent alternation between at least the rotational speed (n) when the pressure falls to the minimum pressure (e) and deactivation of the compressor (3) when the deac-tivation pressure (d) is reached.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102013113557.9A DE102013113557A1 (en) | 2013-12-05 | 2013-12-05 | Compressor system for a railway vehicle and method for operating the compressor system with a safe emergency operation |
| DE102013113557.9 | 2013-12-05 | ||
| PCT/EP2014/076166 WO2015082432A1 (en) | 2013-12-05 | 2014-12-02 | Compressor system for a rail vehicle and method for operating the compressor system with safe emergency operation |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2932783A1 true CA2932783A1 (en) | 2015-06-11 |
Family
ID=52014055
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA2932783A Abandoned CA2932783A1 (en) | 2013-12-05 | 2014-12-02 | Compressor system for a rail vehicle and method for operating the compressor system with safe emergency operation |
Country Status (10)
| Country | Link |
|---|---|
| US (1) | US20170002804A1 (en) |
| EP (1) | EP3077673A1 (en) |
| JP (1) | JP6275257B2 (en) |
| KR (1) | KR20160093649A (en) |
| CN (1) | CN105940221B (en) |
| AU (1) | AU2014359381B2 (en) |
| CA (1) | CA2932783A1 (en) |
| DE (1) | DE102013113557A1 (en) |
| RU (1) | RU2646988C2 (en) |
| WO (1) | WO2015082432A1 (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102015111287B4 (en) * | 2015-07-13 | 2018-04-26 | Gardner Denver Deutschland Gmbh | Compressor and method for its speed control |
| DE102016100705A1 (en) * | 2016-01-18 | 2017-07-20 | Knorr-Bremse Systeme für Schienenfahrzeuge GmbH | Air supply system |
| CN109236659B (en) * | 2018-10-15 | 2020-02-07 | 南京中车浦镇海泰制动设备有限公司 | Control method of oil-free scroll compressor for rail transit wind source system |
| DE102019104760A1 (en) * | 2019-02-25 | 2020-08-27 | Knorr-Bremse Systeme für Schienenfahrzeuge GmbH | Air supply system and method for controlling and / or monitoring an air supply system |
| DE102019131921A1 (en) * | 2019-11-26 | 2021-05-27 | Knorr-Bremse Systeme für Schienenfahrzeuge GmbH | Compressor system for a rail vehicle and method for controlling a cooling device of a compressor system |
| DE102020100296A1 (en) | 2020-01-09 | 2021-07-15 | Knorr-Bremse Systeme für Schienenfahrzeuge GmbH | Compressor system and method for operating a compressor system as a function of the compressed air requirement of an operating state of the vehicle |
| DE102020115300A1 (en) | 2020-06-09 | 2021-12-09 | Knorr-Bremse Systeme für Schienenfahrzeuge GmbH | Compressor system and method for controlling a cooling device of a compressor system |
| DE102021118806B3 (en) | 2021-07-21 | 2022-10-13 | Pierburg Pump Technology Gmbh | Method for controlling an electrically driven fluid pump for a vehicle and an electrically driven fluid pump for a vehicle |
Family Cites Families (26)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2646204A (en) * | 1947-11-13 | 1953-07-21 | Atlas Diesel Ab | Compressor plant |
| DE970770C (en) * | 1950-09-22 | 1958-10-30 | Atlas Copco Ab | Compressor system |
| US3753069A (en) * | 1971-11-18 | 1973-08-14 | Borg Warner | Start-up system for inverter driven motor including inverter bypass circuitry |
| JPS6338693A (en) * | 1986-07-31 | 1988-02-19 | Nippon Air Brake Co Ltd | Pressure regulating method for rolling stock |
| FR2612142B1 (en) * | 1987-03-13 | 1989-05-19 | Alsthom | DEVICE FOR SUPPLYING BRAKE VACUUM OR COMPRESSED AIR BRAKE SYSTEM |
| RU2041393C1 (en) * | 1990-05-17 | 1995-08-09 | Валерий Измаилович Мулуянов | Piston compressor with electrodynamic drive |
| DE4219514A1 (en) * | 1992-06-13 | 1993-12-16 | Reinhold Kuhn | Regenerative braking system for vehicle - has air compressor coupled to transmission during braking or with throttle fully released. |
| JPH07208371A (en) * | 1994-01-13 | 1995-08-08 | Hitachi Ltd | Inverter-driven screw compressor |
| JP3599832B2 (en) * | 1995-06-15 | 2004-12-08 | 兼松日産農林株式会社 | Portable compressor device |
| US6390779B1 (en) * | 1998-07-22 | 2002-05-21 | Westinghouse Air Brake Technologies Corporation | Intelligent air compressor operation |
| BE1013534A5 (en) * | 2000-05-17 | 2002-03-05 | Atlas Copco Airpower Nv | Method voo r controlling a fan in a compressor installation and compressor installation with fan so regulated. |
| US6501629B1 (en) * | 2000-10-26 | 2002-12-31 | Tecumseh Products Company | Hermetic refrigeration compressor motor protector |
| DE10240162A1 (en) * | 2002-08-30 | 2004-03-18 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Air demand controlled compressor arrangement, especially for commercial vehicles |
| JP2004211620A (en) * | 2003-01-06 | 2004-07-29 | Sankyo Seiki Mfg Co Ltd | Pressure control method for compressor |
| DE102004007882B4 (en) * | 2003-03-31 | 2009-12-10 | Hitachi Koki Co., Ltd. | Air compressor and procedures for its controlling |
| JP4069450B2 (en) * | 2003-06-24 | 2008-04-02 | 日立工機株式会社 | Air compressor and control method thereof |
| JP2005069013A (en) * | 2003-08-22 | 2005-03-17 | Tokyo Electric Power Co Inc:The | Gas supply device and its control method |
| US20060045751A1 (en) * | 2004-08-30 | 2006-03-02 | Powermate Corporation | Air compressor with variable speed motor |
| JP2008002380A (en) * | 2006-06-23 | 2008-01-10 | Chikuho Seisakusho:Kk | Additional inverter for compressor |
| DE102007019126B4 (en) * | 2007-04-23 | 2009-07-09 | Knorr-Bremse Systeme für Schienenfahrzeuge GmbH | Sound-enclosed compressor arrangement |
| JP2007285307A (en) * | 2007-08-08 | 2007-11-01 | Hitachi Industrial Equipment Systems Co Ltd | Inverter-drive rotary compressor |
| DE102008007661A1 (en) * | 2008-02-06 | 2009-08-13 | BSH Bosch und Siemens Hausgeräte GmbH | compressor unit |
| US8044310B2 (en) * | 2008-07-16 | 2011-10-25 | Condor-Werke Gebr. Frede Gmbh & Co. Kg | Combination pressure switch |
| JP5410123B2 (en) * | 2009-03-13 | 2014-02-05 | 株式会社日立産機システム | air compressor |
| DE102012223996A1 (en) * | 2012-12-20 | 2014-06-26 | Siemens Aktiengesellschaft | Air pressure generating device for a rail vehicle |
| CN203278743U (en) * | 2013-01-17 | 2013-11-06 | 福建睿能电子有限公司 | Motor frequency conversion controller |
-
2013
- 2013-12-05 DE DE102013113557.9A patent/DE102013113557A1/en not_active Ceased
-
2014
- 2014-12-02 KR KR1020167017034A patent/KR20160093649A/en not_active Application Discontinuation
- 2014-12-02 EP EP14808924.6A patent/EP3077673A1/en not_active Withdrawn
- 2014-12-02 CA CA2932783A patent/CA2932783A1/en not_active Abandoned
- 2014-12-02 WO PCT/EP2014/076166 patent/WO2015082432A1/en active Application Filing
- 2014-12-02 JP JP2016536585A patent/JP6275257B2/en not_active Expired - Fee Related
- 2014-12-02 AU AU2014359381A patent/AU2014359381B2/en not_active Ceased
- 2014-12-02 CN CN201480074101.1A patent/CN105940221B/en not_active Expired - Fee Related
- 2014-12-02 US US15/101,735 patent/US20170002804A1/en not_active Abandoned
- 2014-12-02 RU RU2016126788A patent/RU2646988C2/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| DE102013113557A1 (en) | 2015-06-11 |
| US20170002804A1 (en) | 2017-01-05 |
| EP3077673A1 (en) | 2016-10-12 |
| RU2646988C2 (en) | 2018-03-13 |
| CN105940221B (en) | 2018-02-06 |
| JP6275257B2 (en) | 2018-02-07 |
| AU2014359381B2 (en) | 2017-09-14 |
| WO2015082432A1 (en) | 2015-06-11 |
| JP2016539277A (en) | 2016-12-15 |
| KR20160093649A (en) | 2016-08-08 |
| AU2014359381A1 (en) | 2016-06-23 |
| CN105940221A (en) | 2016-09-14 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request |
Effective date: 20190826 |
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| FZDE | Discontinued |
Effective date: 20220202 |