ES2260285T3 - MULTIPLE STAGE SCREW COMPRESSOR. - Google Patents

MULTIPLE STAGE SCREW COMPRESSOR.

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Publication number
ES2260285T3
ES2260285T3 ES01969980T ES01969980T ES2260285T3 ES 2260285 T3 ES2260285 T3 ES 2260285T3 ES 01969980 T ES01969980 T ES 01969980T ES 01969980 T ES01969980 T ES 01969980T ES 2260285 T3 ES2260285 T3 ES 2260285T3
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Spain
Prior art keywords
compressor
screw compressor
stage
stages
drive means
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Expired - Lifetime
Application number
ES01969980T
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Spanish (es)
Inventor
Philip Nichol
Lyndon Paul Foutain
Terrence Edward Coker
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Compair UK Ltd
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Compair UK Ltd
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/08—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)

Abstract

A multi-stage screw compressor includes at least two stages of compression, each compressor stage including a pair of rotors driven to effect gas compression. Each compression stage is provided with independent variable speed drive means and a control unit for controlling the speeds of the independent drive means. The control unit includes processing means for processing signals generated by a plurality of devices monitoring operating parameters of the compressor, and adjusting the speed of the drive means to provide a required gas flow delivery rate and pressure, at least one of the monitoring devices monitoring the torque and at least one of the monitoring devices monitoring the speed of each drive means.

Description

Compresor de tornillo de etapas múltiples.Multi stage screw compressor.

La invención se refiere a mejoras en el accionamiento de un compresor de tornillo de etapas múltiples utilizando motores eléctricos independientes con control electrónico de la velocidad.The invention relates to improvements in the drive a multi-stage screw compressor using independent electric motors with control electronic speed.

En un compresor de tornillo de etapas múltiples se utiliza habitualmente un dispositivo de accionamiento de velocidad fijo individual para accionar las etapas individuales del compresor simultáneamente a través de una caja de engranajes. Normalmente esto requiere un tren de engranajes de incremento de la velocidad, puesto la velocidad del dispositivo de accionamiento es considerablemente menor que el accionamiento requerido por las etapas del compresor. La velocidad de cada etapa debe adaptarse para conseguir la máxima eficiencia y para compartir el trabajo realizado por cada etapa. Puesto que la relación de transmisión debe cambiarse para efectuar un cambio en el volumen de salida, para permitir proporcionar un rango de diferentes volúmenes de salida a partir de un conjunto común de etapas, se necesita un conjunto de engranajes único para cada salida nominal. Cuando se requiere un rango de presiones finales de suministro diferentes, esto necesita en muchos casos, una relación de transmisión única para cada presión de accionamiento.In a multi-stage screw compressor a drive device of individual fixed speed to drive the individual stages of the compressor simultaneously through a gearbox. Normally this requires a gear train to increase the speed, since the speed of the drive device is considerably less than the drive required by the compressor stages The speed of each stage must be adapted to achieve maximum efficiency and to share work Performed by each stage. Since the transmission ratio must change to make a change in the output volume, to allow to provide a range of different output volumes to Starting from a common set of stages, a set of Unique gears for each nominal output. When a range of different final supply pressures, this needs in many cases, a unique transmission ratio for each pressure drive.

Se puede utilizar un conjunto de etapas del compresor, que funcionan a velocidades diferentes, para dar un rango de flujos de salida de aire. Para obtener un incremento en el flujo de aire, debe incrementarse la velocidad de todas las etapas. Debido a la diferencia en las características de rendimiento de cada etapa, el incremento en la velocidad de cada etapa no será el mismo. Además de esto, la velocidad relativa de las etapas puede tener que ser alterada en función de la presión de suministro de la etapa final deseada o de la relación de la presión general. El parámetro básico que determina la velocidad relativa de las etapas es el trabajo realizado en cada etapa. Para obtener la eficiencia máxima, el trabajo debe ser compensado igualmente en cada etapa.A set of stages of the compressor, which operate at different speeds, to give a range of air outflows. To obtain an increase in air flow, the speed of all stages must be increased. Due to the difference in performance characteristics of each stage, the increase in the speed of each stage will not be the same. In addition to this, the relative speed of the stages can have to be altered depending on the supply pressure of the desired final stage or general pressure ratio. He basic parameter that determines the relative speed of the stages It is the work done at each stage. To get the efficiency maximum, work must be compensated equally at each stage.

El resultado de esto es que para un caudal de aire dado y una presión de suministro dada, debe determinarse un conjunto específico de velocidades para varias etapas de compresión. Una vez determinadas las velocidades, deben seleccionarse los engranajes adecuados. Esto impone una limitación adicional. Debido a la restricción impuesta por la necesidad de tener números enteros de dientes de engranaje, puede no ser posible la relación ideal.The result of this is that for a flow of given air and a given supply pressure, a specific set of speeds for various compression stages. Once the speeds have been determined, the suitable gears This imposes an additional limitation. Because the restriction imposed by the need to have whole numbers of gear teeth, the ideal relationship may not be possible.

Otra consideración es que, para máquinas producidas en serie, el rendimiento de etapas de compresión similares no será idéntico debido a las tolerancias de fabricación, lo que da lugar a variaciones de la holgura. Con relaciones de transmisión fijas, no existe ningún medio para compensar esta variación, que puede afectar de una manera adversa al rendimiento del compresor, puesto que el equilibrio de trabajo entre las etapas no será óptimo. Además, si un usuario desea utilizar un compresor en un trabajo a una distancia desde el punto de diseño, se reducirá la eficiencia de la máquina o, en el caso extremo, se producirá el recalentamiento de las etapas individuales.Another consideration is that, for machines mass produced, compression stage performance similar will not be identical due to manufacturing tolerances, which results in slack variations. With relationships of fixed transmission, there is no means to compensate for this variation, which may adversely affect performance of the compressor, since the work balance between the stages It will not be optimal. Also, if a user wishes to use a compressor in a job at a distance from the design point, it will be reduced machine efficiency or, in the extreme case, the overheating of the individual stages.

Otra consideración es que para proporcionar un control de la capacidad de un compresor de etapas múltiples, se puede utilizar la regulación de la entrada sobre un rango muy estrecho de las velocidades a medida que se incrementa efectivamente la relación de la presión a través de la máquina. Esto conduce de nuevo a recalentamiento. Por esta razón, los compresores de etapas múltiples son controlados habitualmente por el cierre total de la entrada por una válvula de control. Esto proporciona un control muy grosero de la presión o del caudal con eficiencia escasa. La variación de la velocidad del motor de accionamiento ha sido utilizada para controlar algunas máquinas para mejorar la eficiencia con carga parcial. Con una relación fija de las velocidades entre las etapas, esto conduce a un desequilibrio del trabajo entre las etapas, que puede limitar el rango de control.Another consideration is that to provide a capacity control of a multi-stage compressor, it you can use the input regulation over a very range Narrow speeds as it increases effectively the pressure ratio across the machine. This It leads again to overheating. For this reason, the compressors Multi-stage are usually controlled by closing Total input by a control valve. This provides a very rude pressure or flow control with efficiency limited. The variation of the drive motor speed has been used to control some machines to improve the efficiency with partial load. With a fixed ratio of speeds between the stages, this leads to an imbalance of the Work between stages, which can limit the range of control.

Otro ejemplo de un compresor de tornillo de dos etapas, en el que el motor eléctrico de cada etapa es accionado por un accionamiento de velocidad variable, se da por el documento JP 07-158576 A.Another example of a two screw compressor stages, in which the electric motor of each stage is driven by a variable speed drive is given by JP 07-158576 A.

Un objeto de la presente invención es solucionar estos inconvenientes.An object of the present invention is to solve these inconveniences.

De acuerdo con la invención, se proporciona un compresor de tornillo de etapas múltiples como se establece en la reivindicación 1.In accordance with the invention, a multi-stage screw compressor as set forth in the claim 1.

A continuación se describirá una forma de realización preferida de la presente invención, solamente a modo de ejemplo, con referencia a los dibujos que se acompañan, en los que:A form of preferred embodiment of the present invention, only by way of example, with reference to the accompanying drawings, in the that:

La figura 1 es una representación esquemática del funcionamiento de una compresor de tornillo típico de la técnica anterior; yFigure 1 is a schematic representation of the operation of a screw compressor typical of the technique previous; Y

La figura 2 es una representación esquemática de un compresor de tornillo de acuerdo con la presente invención.Figure 2 is a schematic representation of a screw compressor according to the present invention.

En la figura 1 se muestra un compresor de dos etapas 5 de la técnica anterior. Aunque se muestra una máquina de dos etapas, libre de aceite, para mayor claridad, los principios son los mismos donde están implicadas más etapas o donde las etapas tienen inyección de aceite o de agua.A compressor of two is shown in figure 1 Stages 5 of the prior art. Although a machine is shown Two stages, oil free, for clarity, the principles are the same where more stages are involved or where the stages They have oil or water injection.

Cada una de las dos etapas del compresor 10, 11 está constituida por una pareja de rotores estriados, cortados helicoidalmente, a contra-revolución, soportados en cada extremo en cojinetes de rodillos en una carcasa rígida. Cada carcasa está fijada a una caja de engranajes sencilla 12. El motor de accionamiento está acoplado al engranaje de entrada en la caja de engranajes 12, que transfiere el accionamiento a las etapas 10, 11 a través de un piñón sobre los árboles 12a, 12b de cada etapa 10, 11.Each of the two stages of the compressor 10, 11 It consists of a pair of striated rotors, cut helically, counter-revolution, supported in each end in roller bearings in a rigid housing. Every housing is fixed to a simple gearbox 12. The engine drive is coupled to the input gear in the box of gears 12, which transfers the drive to stages 10, 11 through a pinion on the trees 12a, 12b of each stage 10, eleven.

Se aspira aire a través de un filtro de aire 14 y a través de la válvula de control de entrada 15 en el orificio de entrada de la primera etapa 10, donde se comprime parcialmente. El aire parcialmente comprimido desde la primera etapa 10 pasa a un termocambiador intermedio 16, donde se reduce su temperatura antes de que el aire pase hasta la entrada de la segunda fase 11 para compresión adicional. Después de abandonar la segunda etapa 11 (o final), el aire totalmente comprimido pasa a través de una válvula de control 17 hasta un refrigerador posterior 18 para la refrigeración posterior, después de lo cual se suministra al usuario a través de la salida de suministro de aire 19.Air is sucked through an air filter 14 and through the inlet control valve 15 in the orifice of entrance of the first stage 10, where it is partially compressed. He partially compressed air from the first stage 10 passes to a intermediate heat exchanger 16, where its temperature is reduced before that the air passes to the entrance of the second phase 11 to additional compression After leaving the second stage 11 (or end), the fully compressed air passes through a valve control 17 to a rear refrigerator 18 for subsequent cooling, after which it is supplied to the user through the air supply outlet 19.

En esta forma de realización, el termocambiador intermedio 16 y el refrigerador posterior 18 son refrigerados cada uno de ellos por aire ambiente que es impulsado sobre ellos por un ventilador 20 accionado por motor. Una alternativa consiste en utilizar intercambiadores de calor refrigerados con agua.In this embodiment, the heat exchanger intermediate 16 and the rear refrigerator 18 are refrigerated each one of them by ambient air that is driven on them by a 20 motor driven fan. An alternative consists of use heat exchangers cooled with water.

La figura 2 muestra un compresor 30 de acuerdo con la presente invención. La operación esencial es como se ha descrito anteriormente, pero difiere del compresor 5 de la técnica anterior porque motores 31, 32 independientes de velocidad variable accionan cada una de las etapas 10, 11 del compresor de una manera independiente, sin ningún enlace mecánico entre las etapas 10, 11 accionadas por motores individuales. Las características de los motores 31, 32 están adaptadas a las etapas correspondientes de los compresores 10, 11.Figure 2 shows a compressor 30 according with the present invention. The essential operation is as it has been described above, but differs from the compressor 5 of the technique previous because 31, 32 independent variable speed motors they operate each of the stages 10, 11 of the compressor in a manner independent, without any mechanical link between stages 10, 11 driven by individual motors. The characteristics of the engines 31, 32 are adapted to the corresponding stages of the compressors 10, 11.

La velocidad de los motores 31, 32 está controlada por un controlador electrónico 33. El parámetro básico de control es la presión final de suministro de aire o el caudal de suministro de aire. La velocidad a la que se acciona cada una de las etapas 10, 11 se incrementa para proporcionar un caudal mayor o se reduce para proporcionar menor caudal de aire. Las velocidades de giro máximas están limitadas a niveles predeterminados basados en consideraciones mecánicas. Las velocidades mínimas o bien están pre-determinadas o son determinadas midiendo las temperaturas de suministro de cada etapa 10, 11. A medida que se reduce la velocidad de los rotores de cualquier etapa, la etapa se vuelve menos eficiente, provocando una subida de la temperatura. Cuando ésta alcanza un valor máximo pre-ajustado, el compresor 30 se para o se descarga a través de una válvula de entrada 15.The speed of the engines 31, 32 is controlled by an electronic controller 33. The basic parameter control is the final air supply pressure or flow rate of air supply. The speed at which each one is operated stages 10, 11 is increased to provide a higher flow rate or It is reduced to provide lower air flow. Speeds Maximum turning limits are limited to predetermined levels based in mechanical considerations. The minimum speeds are either pre-determined or are determined by measuring the Supply temperatures of each stage 10, 11. As you reduce the speed of any stage rotors, the stage is It becomes less efficient, causing a temperature rise. When it reaches a pre-set maximum value, the compressor 30 stops or is discharged through a valve entry 15.

Para mantener una eficiencia óptima en todas las condiciones, se varían las velocidades de las etapas individuales del compresor 10, 11 para compensar una variedad de factores. Estos factores incluyen altitud, presión barométrica, temperatura ambiente y temperatura del refrigerante, bloqueo de los filtros y desgaste. También se compensan las variaciones de fabricación en las etapas del compresor 10, 11.To maintain optimum efficiency in all conditions, the speeds of the individual stages are varied of compressor 10, 11 to compensate for a variety of factors. These factors include altitude, barometric pressure, temperature ambient and coolant temperature, filter blocking and wear. Manufacturing variations are also compensated in Compressor stages 10, 11.

Este control se consigue midiendo continuamente las presiones de suministro de aire y las temperaturas desde cada etapa 10, 11 así como el par motor de entrada y la velocidad a cada etapa 10, 11. Se utilizan dispositivos de medición adecuados para medir estos parámetros y transmitir señales al controlador electrónico 33. Los motores 31, 32 pueden tener bucles de realimentación directamente al controlador 33. El controlador 33 procesa las señales y ajusta la velocidad de las etapas 10, 11 para conseguir el caudal de aire y la presión de suministro deseados. Luego, utilizando las mediciones descritas anteriormente, el controlador 33 realiza ajustes pequeños a las velocidades de las etapas para reducir al mínimo el consumo de potencia, igualar el trabajo entre las varias etapas y mantener las temperaturas de servicio de seguridad.This control is achieved by continuously measuring air supply pressures and temperatures from each stage 10, 11 as well as the input torque and speed at each step 10, 11. Suitable measuring devices are used to measure these parameters and transmit signals to the controller electronic 33. Motors 31, 32 may have loops of feedback directly to controller 33. Controller 33 process the signals and adjust the speed of stages 10, 11 to achieve the desired air flow and supply pressure. Then, using the measurements described above, the controller 33 makes small adjustments to the speeds of the stages to minimize power consumption, match the work between the various stages and maintain the temperatures of security Service.

Aunque la descripción anterior se refiere solamente a compresores de aire, debería entenderse que esta invención se puede utilizar también para compresores para otros gases.Although the above description refers only to air compressors, it should be understood that this invention can also be used for compressors for others gases

Claims (5)

1. Un compresor de tornillo de etapas múltiples (30) que comprende:1. A multi-stage screw compressor (30) comprising: dos o más etapas del compresor (10, 11), en las que cada etapa del compresor comprende una pareja de rotores para comprimir un gas;two or more compressor stages (10, 11), in the that each stage of the compressor comprises a pair of rotors for compress a gas; dos o más medios de accionamiento de la velocidad variable (31, 32), donde cada uno de los medios de accionamiento de la velocidad variable (31, 32) es operativo para accionar una etapa del compresor (10, 11) respectiva; ytwo or more means of actuation of the variable speed (31, 32), where each of the means of Variable speed drive (31, 32) is operational for actuate a respective compressor stage (10, 11); Y una unidad de control (33) que comprende medios de procesamiento operativos para procesar señales indicativas de parámetros de funcionamiento del compresor de tornillo (30) y para controlar las velocidades de los medios de accionamiento de la velocidad variable (31, 32), caracterizado porque:a control unit (33) comprising operational processing means for processing signals indicative of operating parameters of the screw compressor (30) and for controlling the speeds of the variable speed drive means (31, 32), characterized in that : el compresor de tornillo comprende dispositivos de supervisión operativos para supervisar el par de torsión y la velocidad de cada uno de los medios de accionamiento de la velocidad variable (31, 32),the screw compressor comprises devices operational monitoring to monitor the torque and the speed of each of the speed drive means variable (31, 32), la unidad de control (33) es operativa para controlar las velocidades de los medios de accionamiento de velocidad variable (31, 32), de manera que el compresor de tornillo (30) proporciona gas a un caudal de suministro y presión requeridos, y porquethe control unit (33) is operative for control the speeds of the drive means of variable speed (31, 32), so that the screw compressor (30) provides gas at a required supply flow and pressure, and because la unidad de control (33) es operativa para procesar señales indicativas del par de torsión y de la velocidad de cada uno de los medios de accionamiento de velocidad variable (31, 32) y para controlar las velocidades de los medios de accionamiento de velocidad variable (31, 32), de manera que se reduce substancialmente al mínimo el consumo de potencia del compresor de tornillo (3).the control unit (33) is operative for process signals indicative of torque and speed of each of the variable speed drive means (31, 32) and to control the media speeds of variable speed drive (31, 32), so that substantially reduces the power consumption of the screw compressor (3). 2. Un compresor de tornillo (30) de acuerdo con la reivindicación 1, que comprende, además, dispositivos de supervisión para supervisar las temperaturas de suministro del gas en cada etapa del compresor (10, 11).2. A screw compressor (30) according to claim 1, further comprising devices of supervision to monitor gas supply temperatures at each stage of the compressor (10, 11). 3. Un compresor de tornillo (30) de acuerdo con una cualquiera de las reivindicaciones anteriores, que comprende, además, al menos un dispositivo de supervisión de la temperatura ambiente.3. A screw compressor (30) according to any one of the preceding claims, comprising, in addition, at least one temperature monitoring device ambient. 4. Un compresor de tornillo (30) de acuerdo con una cualquiera de las reivindicaciones anteriores, que comprende, además, medios de refrigeración (16) previstos entre etapas del compresor (10, 11) adyacentes y al menos un dispositivo de supervisión para supervisar la temperatura del gas después de pasar a través de los medios de refrigeración (16).4. A screw compressor (30) according to any one of the preceding claims, comprising, in addition, cooling means (16) provided between stages of the adjacent compressor (10, 11) and at least one device supervision to monitor the gas temperature after passing through the cooling means (16). 5. Un compresor de tornillo (30) de acuerdo con una cualquiera de las reivindicaciones anteriores, que comprende, además, al menos un dispositivo de supervisión para supervisar la presión de suministro del gas en cada etapa de compresión (10, 11).5. A screw compressor (30) according to any one of the preceding claims, comprising, in addition, at least one monitoring device to monitor the gas supply pressure at each compression stage (10, eleven).
ES01969980T 2000-09-25 2001-09-25 MULTIPLE STAGE SCREW COMPRESSOR. Expired - Lifetime ES2260285T3 (en)

Applications Claiming Priority (2)

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GB0023456A GB2367332B (en) 2000-09-25 2000-09-25 Improvements in multi-stage screw compressor drive arrangements
GB0023456 2000-09-25

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ES2260285T3 true ES2260285T3 (en) 2006-11-01

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US (1) US20040101411A1 (en)
EP (1) EP1387961B1 (en)
AT (1) ATE319932T1 (en)
AU (1) AU2001290100A1 (en)
DE (1) DE60117821T2 (en)
ES (1) ES2260285T3 (en)
GB (1) GB2367332B (en)
WO (1) WO2002025115A1 (en)

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AU2001290100A1 (en) 2002-04-02

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