DE2303260A1 - BEARING ARRANGEMENT FOR HIGH SPEED MACHINERY - Google Patents

Description

Bormalair-Garrett (Holdings) Limited, Vcstland Works, Veovil, Somerset, England

Bearing arrangement for machines rotating at high speed.

The present invention "relates to machines that work with rotate at high speed, especially (but not exclusively) on turbine units.

The object of the present invention is the period between two maintenance processes in machines rotating at high speed to increase thereby that a loss of the lubricant or lubricant for the bearings of the x'otierenden element of the Haschine is completely or almost completely avoided. At the same time, funds should be provided with which at least a certain cooling effect for one or also for several elements of the rotating device is achieved.

To solve this problem, a bearing arrangement for with

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holier speed rotating machines with a supported by bearings rotating element and with a lubrication system for these bearings according to the invention a lubrication chamber through which the rotating element extends, wall parts that enclose the bearings and the lubrication system between them, inner Sealing means cooperating with the wall parts and a surface of the rotating element, a channel arrangement which extends towards the rotating element and is arranged on the outside of the wall parts and a chamber for a static Pressure forms, external sealant that is in operative connection with the channel arrangement and the surface of the rotating element are, with an inlet for a pressurized medium in the channel arrangement is possible, as well as openings for the passage of this medium on both sides through the outer Sealant on.

The present invention is described below with the aid of an exemplary embodiment explained in more detail in connection with the figure, which shows a section through a turbine unit, as it is for example is used in an air circuit cooling system.

The turbine unit consists of a turbine 10 and a Compressor 11, both of which are mounted on a common shaft 12, which is mounted on two races 13 within the bearing bracket 14 are stored. The bearing bracket 14 is in turn inside of the two, the main part of the machine. forming parts 15 and 16, which are the essential elements of a closed Eaum-forming arrangement. The closed iiaum contains means for lubricating the bearings or races 13- Am Part 15 is a combined turbine inlet and outlet connection piece 17 attached, while the part 16 with a combined

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Coinpressor inlet and outlet connector 18 is connected. The means for lubricating the bearing or race 13 include an annular lubricant reservoir 19, v / which forms a rope of the closed space and in a suitable Veise with absorbent material is filled and through which a wick 20 hiiidureh 'is carried out. The wick 20 extends through the bearing bracket 1'i- through and is in contact with two annular, oblique to the axis of the Welles. 12 running surfaces "21 on this Shaft which is anox'diiet on the inner sides of the bearing or race rings 13 are. On the outside of each running ring 13, namely still within the closed space, there is a wing or Impeller 22 attached to shaft 12. In the area of the rotating shaft 12 is the closed space with the help of labyrinth seals 23 sealed between the hub of each impeller or impeller 22 and a radial wall 24, 25 are formed, which latter part of the parts 15 "and 16 are.

For circulation from the area of the inclined surfaces 21 of the shaft, through the bearings or races 13 to the impellers or paddle wheels 22 and from there into the annular outer chamber 26 of the bearing carrier 1-4 and back into the area around the inclined Surfaces 21 are circulation openings through the bearings or races 13, from the impeller or paddle wheels into the Kam-IBr 26 and from this chamber into the area around the inclined surfaces 21 in the middle between these surfaces. On the outside of the labyrinth seals 23, which are hereinafter referred to as "inner seals", a chamber 27 or 28 for a high pressure or a static pressure is provided, these chambers from the radial walls 2A- and 25 and each of an inner element 29 or 30

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external sealant ". The chambers 27 and 28 . are interconnected by a channel 31, for example is formed by bores in parts 15 and 16 «In the one chamber 28, a centrifugal pump 32 is provided on the shaft 12, which via bores in "the shaft 12 with the , Inside the bearing bracket 14, in the area between the inclined surfaces 21, is in connection. The outer sealants also include outer members 33 and 34 that have a certain Have a distance from the inner elements 29 and 30 and in this way each form a disc-shaped channel 35, which is arranged concentrically to the shaft 12 and through which air can be supplied to the shaft. The inner and outer Elements. 29, 30? 33 and 34 have depressions and that in such a way that they form labyrinth seals, the recesses on elements 29 and 33 acting as seals with the hub of the turbine wheel and the recesses of elements 30 and 34 in similarly cooperate as seals with the hub of the compressor wheel. A channel 36 connects the two disk-shaped ones at 37 Channels 35- with the inlet part of the turbine inlet and Auslaßverbiiidungsstückes 17 "with the opening 37," based on the flow through the turbine, in front of the turbine nozzles.

During operation, the turbine input is supplied with compressed air and _v released through the nozzle of the turbine so as to expand along the turbine wheel and to drive the compressor to supply compressed air in this manner. The bearings or the running rings 13 are lubricated with the help of the wick 20, which contains oil from the oil-soaked, absorbent material in the reservoir 19 and brings it to the inclined surfaces 21 of the shaft 12, where centrifugal forces cause the oil from the wick 20 is carried away and thrown away as a lever from the shaft to the outside. The vanes or paddle wheels 22 leading to the ends of the

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Shaft Mn are offset with respect to the bearings or races 13, suck this lever through the bearings or races 13 and cause that this lever through the Sirkulatioiiswege, which enclose the annular outer chamber 26 of the bearing bracket 14, returns to the area around the shaft between the inclined surfaces 21. Loss of lubricant is avoided with the help of the inner seals 23 prevented, along which a pressure difference is maintained, the area of higher pressure on the outside in the chambers 27 and 2C for the static pressure is located. The higher pressure is diverted at 37 in front of the turbine nozzles from the air that enters the turbine is supplied, and is via the channel 36 in the disk-shaped Channels 35 routed. Small openings allow higher pressure air through the labyrinth seals of the inner and outer Elements 29, 33 and 30, 34 · »cLie the hubs of the turbine and Compressor wheel are adjacent to the outside on the one hand in the chambers 27 and 28 and on the other hand to the rear of the corresponding Wheels penetrate. Since chambers 27 and 28 have no exit own, they contain a static pressure, while at the back of the turbine wheel or the compressor wheel constant air flow is achieved. This air flow then either reaches a turbine area around the edge of the turbine wheel with low pressure behind the turbine nozzles, or around the edge of the compressor wheel in a compressor area with low pressure in front of the diffuser guide vanes Compressor. To get a pressure drop that is independent of pressure changes in the system is a centrifugal pump 32 is provided, which strives to remove air from the closed space to promote into the chamber 28 through the bores in the shaft. ' The pressure reduction achieved with this pump 32 is, however depending on the static pressure in the chamber 28. With the help of the connecting channel 31, 27 and 28 for both chambers equally high pressure achieved. Through the air behind the

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When the compressor wheel is passed along, there is a certain amount of cooling achieved this wheel, the strength of this air flow through the annular gap between the labyrinth seal of the outer Element 34- and the property of the compressor wheel "is determined.

A large number of changes or modifications are conceivable, without departing from the scope of the present invention. For example, the pressure for the seals from another place within the, at high speed rotating machine, or the pressure is supplied by an independent pressure source and the channel supplied, with a 'temperature control if necessary is provided. Even if the invention is based on a turbine arrangement has been explained in more detail, it goes without saying that pressure seals according to this Ex-finding can also be used in other types machines rotating at high speed can be used.

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Claims (1)

I: / p 7569 -7- · 1/19/73 P atei ita μ s p "r ü c Ii e Bearing arrangement for high-speed rotating machines, with bearings for a rotating element and with a lubrication system for these bearings characterized by an ochiniex ^ kainmor, entroll vrelche the rotating element (12) extends through v \ Ta: nateile (24, 25) . which the bearings and the lubrication system are enclosed by internal sealing means (23) which connect to the handle parts (24, 2 ^) and a surface (22) of the rotating jileHontes (12), through a channel arrangement ( 2 ^! /, 28), which extends towards the rotating element (12) and is arranged on the outside of the wall parts (24, 25) and forms hammering for a static pressure , through external sealing means (29, 330, 35 , 54), which are connected to the duct arrangement (27, 26) and with the surface of the rotating element (12), whereby an ileus under pressure can enter the ivaiial anoxic system (27, 28) , and through openings for the passage of the ilium through the outer sealing means (29, 30, 35 - 5 "- J after both 2. Bearing arrangement according to claim 1, characterized in that the channel arrangement (27, 2G) of swei at a distance from one another extending radial walls (24, 25, 29, 30) is formed « 3- bearing assembly of claim 1 or 2, characterized in that the inner (23) and the outer (29, 30, 335 3 0 ^ sealing means are designed as AEE ¹ with the surface of the rotating element (12) labyrinth seals. ^; .. Bearing arrangement according to one of claims 1 to 3, characterized in that the lubricant container via a centrifugal pump 309832/0 8 98 Ν / ρ? 569 ^; · ■ -8-. 19.1.73 G / We (32) with the chamber. (28) for static pressure in 7-bond stands-. 5. Bearing arrangement according to one of claims 1-4, characterized in that that when using them in a turbo compressor unit the duct arrangement (27, 28) with a turbine section is in. Connection, which has high pressure and in front of the nozzles of the, the rotating element (12) driving turbine (lO) .- is located. . . 6. Bearing arrangement according to claim 5, characterized in that the outer sealing means (34-) near the compressor wheel (11) on the rotating element (12) are designed so that a flow of the pressurized through small openings Medium reaches the rear of the compressor wheel (11). 309832/0898