DE1503658C - Centrifugal compressors, especially for refrigeration units? - Google Patents

Description

3 4

processing ring 25 is mounted, which in turn is held on the. In its cylindrical outer surface 31

neren end of the intake 10 is arranged. the annular wall 30 has an annular groove 65 into which in

The impeller is seated on a shaft 22, with the pins 66 provided by the housing jacket 34

Intervene not shown electric motor via a translation game. The pins limit the axial displacement

tongue gear is driven. 5 Slidability of the ring wall in the housing jacket.

The impeller is of an annular diffuser. The impeller shaft 22 has an axial journal 26 surrounded, which in a spiral-shaped Auslaßka- 60 of smaller diameter, whose end with Genal 29 empties. Diffuser and outlet duct are provided with a thread and a screw on it the opposite to the inlet port 10 ter 61 carries with a "streamlined cap Side limited by a plate 28, while on the io 62 is provided and the impeller 20 on the shaft 22 the other side of the diffuser is secured by an annular wall 30.

and the outlet duct of a housing ring 37 operates the compressor at full power, so limited are. The annular wall 30 has a cylindrical shape, the guide vanes 12 are in a fully open position Drischen approach 31 on, with which it is in a zylin- position, and the diffuser 26 is at its largest Drischen bore 32 of an approximately cylindrical, the 15 width set, as shown in F i g. 1 is shown. The intake port 10 surrounding the housing jacket 34. If the performance of the fan is to be reduced, so is slidably mounted. The housing jacket 34 is pressurized oil through the channel 52 into the annulus introduced via a flange by means of screws 35 on the ring 50. As a result, the annular piston 41 shaped end face of an adjoining housing moved inward. He turns over the crank pin 36 attached that the plate 28 and the ring 37 surround 16 the guide vanes 12 in the closing direction. Will closes. On the inner surface of the housing jacket 34, the annular piston moves so far that the Leitschauist an inwardly protruding flange 39 is provided, between which it almost reaches its closed position, so it strikes see its cylindrical inner surface 38 and one of it as it moves against the ring insert cylindrical outer surface 42 of the intake port 10 '56 and takes this and the annular wall 30 with whereein Ring piston 41 narrowed with its outer surface 40 and 25 through the passage of the diffuser 26 and the its inner surface 43 is slidably disposed. Speed of the gases flowing through it, the The end 44 facing away from the fan impeller 20 beforehand by the closing movement of the guide vanes the ring piston is reinforced outwards and slides have been decreased, increased again. This prevents of its outer cylindrical surface 45 on a cylinder, the pressure surges mentioned at the beginning, which otherwise drical inner surface 46 of the housing jacket 34. 30 occur when the delivery rate is reduced. is

Between the annular piston 41 and the casing 34, the annular piston 41 is pushed so far inwardly, there is an annular space 48, which has been passed over a channel 49 provided in the casing casing so that the guide vanes have reached their closed position, so it moves the annular wall 30 A pressure oil line (not shown) is also connected, which is further inward and finally narrows the diffuser. Between the intake 10 and the 35 on the in F i g. 2 position shown.
The housing jacket 34 is located before the increased a pressure oil line, not shown, connected 50 is relieved. As a result, the annular piston ^ls t · 40 41 is moved outwardly, causing the guide vanes 12

The crank pins 16 of the guide vanes 12; grab again opens. The ring wall 30 follows this

into an annular groove 54 of the annular piston 41! In the annular piston under the influence of the diffuser

Annular wall 30 is an annular insert 56 visible pressure until it meets the side wall of the

sets, which abuts against the stop pins 66 through a snap ring 59 in its position annular groove 65.

1 sheet of drawings

Claims (5)

1 2 sucked in gas a more or less strong patent claims: give swirl and with constant speed of the impeller the delivery rate of the compressor so 1. Radial compressors, especially for cooling units, can prevent the diffuser cross-section from becoming too large for gregate with pump-free operation arranged in the axial intake port. There arise Neten, by means of an actuator together from then pulsating shocks in the impeller, which cause vibrations of the open position in a throttle or and annoying noises.
It is also known to regulate the output of a diffuser and centrifugal compressor that surrounds the impeller by changing the diff through the iofusors flowing out of the impeller. For this purpose, it has been provided that gases are put into a spiral pressure channel - a boundary wall of the diffuser is axially adjustable, characterized in that it is to be arranged, for example, in the form of an annular piston carrying the boundary diffuser (26) in a known manner through the axial wall, which at its Axial wall displacement, cross-sectional variable displacement, changes the passage of the diffuser, is formed and its partition (30) is equipped with the adjustable guide vanes (12) via an actuator diffuser with a guide vane ring, (41 ) is coupled, whereby the cross-section reducer with its guide vanes does not begin to change the diffuser due to the diffuser until the guide-flowing medium gives an additional swirl, and the blades (12) are almost closed. The invention is based on the object 2. Centrifugal compressor according to claim 1, characterized 20 in the power control of centrifugal compressors characterized in that the in Shovel (12) serving actuator from a guide compressor housing adjustable in a throttle or closed position (10, 34) axially displaceable, blades due to insufficient adjustment of the diffuhydraulic actuated annular piston (41) exists, sor cross section to the reduced delivery rate to eliminate the instability that occurs towards the end of its closing of the guide vanes, which is the case with small scoops serving movement against the setting of the power previously pulsating shocks in the wall (30) of the diffuser (26) and pushes them into the impeller and the associated vibrations and the diffuser cross-section narrowing position causes noises. brings. This object is achieved according to the invention 3. Centrifugal compressor solved according to one of the previous 30, that with a centrifugal compressor with the loan end Claims, characterized in that the capacity control is arranged in the axial intake port movable partition (30) of the diffuser th, adjustable in a throttled or closed position Anren guide vanes arranged in their adjustment area and one that surrounds the impeller (65, 66) on a limited diffuser that partially adjusts the diffuser in a known manner ment is limited. 35 cross-section changes due to axial wall displacement 4. Centrifugal compressor according to claim 3, characterized in that it is designed and its partition is marked with the that the displaceable diffuser-adjustable guide vanes are coupled via an actuator wall (30) in its cylindrical outer surface is a, the cross-sectional reduction of the diffu-annular groove (65), which only begins in the compressor when the guide vanes are already approaching (10, 34) provided stop pins (66) are closed at 4 °. intervention. Preferably there is to adjust the 5. Centrifugal compressor after one of the previous guide vanes serving actuator from a silting up Claims, characterized in that the seal housing axially displaceable, hydraulically bean Crank cheeks (15) arranged crank pin actuated annular piston, which towards the end of its for (16) of the guide vanes (12) in an annular groove (54) 45 closing the guide vanes serving movement gedes Engage the actuator (41). gen against the partition wall of the diffuser and push it into the brings the diffuser cross-section narrowing position. In the drawing, a centrifugal compressor is shown in accordance with of the invention shown for example, namely The invention relates to centrifugal compressors, 50 shows especially for cooling units, with an axial start. 1 shows an axial section through the compressor arranged suction port, by means of an actuator with fully open guide vanes and narrowest stel together from the open position to a throttling of the diffuser and or closed position adjustable guide vanes and F i g. 2 shows an excerpt from FIG. 1 in larger a diffuser surrounding the impeller, by a scale with closed guide vanes and narrowest the gases flowing out of the impeller in the position of the diffuser.
enter a spiral pressure channel. The compressor housing is equipped with an intake In such compressors, the impeller is provided zen 10, which is a conically tapered Usually enclosed by an annular diffuser around suction duct 11. At the inner end of the enter, which is discharged into a spiral pressure duct 60 suction duct is a ring of guide vanes 12. Usually the diffuser is arranged for the maxi- The guide vanes sit radially in the Stutmale Measure the delivery rate of the compressor. Verzen mounted axles 14, each with one on the outside denser for refrigeration units must be provided via a crank web 15, which has an eccentric size Area to be adjustable in their delivery rate see crank pin 16 carries. and are for this purpose in their axial intake port 65. The impeller 20 of the compressor 18 is usually with radial with a wreath of adjustable. len blades 19 provided. Towards the suction side Provided guide vanes, which rotate around radial axes, the impeller is made of a curved ring disk are stored in bar and, depending on their setting, the 21 is limited, which is connected to a seal with a ring 24