A ROTARY MACHINE EQUIPPED WITH A THRUST BALANCING ARRANGEMENT

Abstract: Rotary machine which comprises a housing having a low-pressure side and a high-pressure side (3) and incorporating working-fluid inlet and outlet channels, at least one rotor (7) urged by the working fluid towards the low-pressure side, and a thrust balancing arrangement (15, 16) incorporating an auxiliary bearing (17). The auxiliary bearing (17) is mounted on an outer-most part of the rotor journal shaft (18), on the high-pressure side (3) of the rotor, between, on the one hand, a locking device (27) intended for the auxiliary bearing (17) and removably mounted on the journal shaft, and the thrust balancing arrangement on the other, this thrust balancing arrangement being located inwards of the auxiliary thrust bearing and having the form of two annular parts (15, 16) which are axially extendible in a known manner and which are located in a cylindrical recess (14) in the housing.

Description: A rotary machine equipped with a thrust balancing arrange¬ ment. The present invention relates to a rotary machine of the kind set forth in the preamble of claim 1. A machine of this kind comprising two helical rotors which are journalled in thrust bearings at both ends thereof is known from US Patent Specification 3 388 854. In order to obtain uniform distribution of the load on the thrust bearings and a long useful bearing life, while avoiding the transition to larger bearings - which normal¬ ly presents a problem due to the lack of space for accom¬ modating bearings of larger diameter - the known machine is provided with a thrust balancing arrangement comprising a piston-cylinder device which under the influence of pressure fluid contingent on one working condition of the machine exerts an axial thrust on one rotor through the thrust bearing on the low pressure side of the machine. This axial thrust is exerted in a direction opposite to the direction in which the working fluid acts and also in an opposite direction to the bias of a spring means acting on the thrust bearing. The length of the useful life of the machine depends upon the condition of the thrust bearings. The bearings need to be inspected at regular intervals and must be changed when necessary. A bearing change is difficult to carry out and requires skill and experience on the part of the engineer concerned. For example, when effecting a bearing change it is necessary to dismantle the thrust balancing arrangement, together with associated connections and seals, and then to reassemble the thrust balancing ar¬ rangement and test the efficiency of the seals, which in- volves further work and also the risk of faults occurring aε a result of dismantling the thrust balancing arrange¬ ment, etc. The object of the present invention is to provide a ma¬ chine of the aforementioned kind in which the thrust balancing arrangement is constructed in a manner which will enable the thrust bearing to be checked and changed without undue difficulty, and which will extend the use¬ ful life of the thrust bearings. This object is achieved in accordance with the invention with a machine having the characteristic features set forth in the characterizing clauses of the following claims. The fact that the auxiliary thrust bearing is located on the extremity of the shaft journal and is clamped resil- iently between the thrust balancing arrangement and the spring means, enables the thrust bearing to be checked an d changed easily, even by unskilled workmen. The rela¬ tive ease with which the auxiliary bearing can be replaced can be utilized suitably by placing a relatively heavy load on the auxiliary thrust bearing and by lessening the load on the remaining bearings to a corresponding extent, therewith prolonging the useful life of the bearings. The auxiliary bearing on the other hand, enjoys a shorter useful life. This is of minor importance, however, since the auxiliary bearing can be readily changed, for instance when carrying out routine maintenance service. The auxiliary thrust bearing may also be active when starting and stopping the machine, when the working fluid is under no pressure, or only a slight pressure, i.e. at low speeds which result in unproportional wear on the bearing. This is a further reason as to why it should be easy to replace the auxiliary thrust bearing. According to one preferred embodiment of the invention, the annular piston-cylinder device of the thrust balancing arrangement has the form of a "plug-in" unit, therewith enabling said device to be readily removed and replaced without risk of causing a leakage as a result thereof. The invention will now be described in more detail with reference to exemplifying embodiments thereof illustrated in the accompanying schematic drawings, in which Figure 1 is a side view of a machine constructed in ac¬ cordance with the invention; Figure 2 is a longitudinal, sectional view of the bearing arrangement on the high-pressure side of the machine; and Figure 3 is a part sectional view showing a modification to the auxiliary bearing illustrated in Figure 2. Figure 1 illustrates very schematically a screw compressor which comprises a housing 1 which has a low-pressure side 2 and a high-pressure side 3, and which incorporates a working-fluid inlet channel 4 and a working-fluid outlet channel 5, the working fluid being a refrigerant for exam¬ ple. Journalled for rotation in the housing 1 are two helical rotors 6, 7. As shown in Figure 2, which is a horizontal, sectional view taken through the geometric centre line of the rotor shafts, a journal shaft 8 on the high-pressure end of the right-hand rotor 7, which is a male rotor and is seen from above, is journalled primarily in a radial bearing 10 and two mutually matching thrust ball-bearings 11. Despite the difficulties involved with the illustrated arrangement of double, so-called matched ball-bearings 11, such an arrangement is necessary due to the high axial forces to which the bearings are sub¬ jected and the requirement of a long useful life of the bearings, and because the space around the journal shaft 8 on this end of the rotor is restricted and cannot ac¬ commodate the use of larger thrust bearings. The bearing arrangement is located in a cylindrical recess 14 in the high-pressure end 3 of the housing. The recess 14 also accommodates a thrust balancing arrangement in the form of an annular piston-cylinder device 15, 16, which is mounted for sliding movement in the recess. Also arranged for sliding movement in the recess 14, axially outwards of the piston-cylinder device 15, 16, is the outer ring of an auxiliary bearing 17 and a distance sleeve 18 which abuts resiliently against a cup spring 19 located on the inside of a cover plate 20, which closes the recess 14. Mutually facing surfaces of the piston 15 and cylinder 16 define therebetween an annular chamber 21 which communi¬ cates with a pressure-medium channel 22 extending through the wall of the housing 1 and which accommodates a thrust spring which holds the components apart. In order to prevent pressure fluid leaking from the chamber 21, the piston 15 is provided with a sealing ring 23 which seals against the recess 14, whereas the cylinder 16 is provided with a first sealing ring 24, which seals against the re¬ cess 14, and a second sealing ring 25, which seals against the piston 15. The inner rings of the radial bearing 10 and the thrust bearings 11 r a distance sleeve 26, and the inner ring of the auxiliary thrust bearing 17 are clamped on the journal shaft 8 by means of a lock plate 27 which is firmly screwed onto the end of said shaft. The auxiliary bearing 17 is of the kind which is able to transfer thrust in both directions. When the rotary ma¬ chine is stationary or when the pressure acting on the fluid in the chamber 21 is low, the rotor 7 is held pressed towards the low-pressure side 2 of the cup spring 19, the force of which is transmitted to the rotor 7 through the distance sleeve 18, the auxiliary bearing 17, the distance sleeve 26, and the inner rings of respective bearings 11. When the rotor machine is started and begins to build up speed, the pressure exerted by the working medium on the end surfaces of the rotors 6, 7 on the high-pressure side will increase, therewith increasing the load on the thrust bearings 11. The pressure acting on the fluid in the chamber 21 will also increase at the same time, causing the piston 15 to be brought into abutment with the outer rings of respective bearings 11 and the cylinder 16 to be brought into abutment with the outer ring of the auxiliary bearing 17, against the action of the cup spring 19. The lock plate 27, and therewith the whole of the rotor 7, will thus be urged towards the high-pressure side 3 of the machine, therewith reducing the load on the bearings 11. By mutually adapting the pressure in the chamber 21 and the area of the cylinder 16 in said chamber, it is possi¬ ble to distribute the load exerted axially by the rotor 7 on the bearings 11 and the auxiliary bearing 17 in a man- ner which will afford the requisite length of useful life of the bearings 11. It is possible to accept, without detriment, a relatively heavy load on the auxiliary bear¬ ing 17, which also has to take-up the load exerted by the cup spring 19, since the auxiliary bearing can be changed readily as a matter of routine when carrying out a service, without involving either the bearings 11 or the piston- cylinder device 15, 16 and its connection 22. Removal of the cover plate 20 and the lock plate 27 enables the sleeve 18 and the auxiliary bearing 17 to be withdrawn from the recess 14. If necessary it is also possible to withdraw the thrust balancing arrangement 15, 16 without needing to touch the pressure-fluid connection. The auxiliary bearing need not be a bearing of the kind illustrated in Figure 2, which is capable of taking up axial loads in both directions, but may comprise two sepa¬ rate bearings, for instance as illustrated in Figure 3. With regard to the balancing of thrust, the Figure 3 em¬ bodiment includes a bearing 30 which corresponds to the bearing 17 of the Figure 2 embodiment. However, the em¬ bodiment illustrated in Figure 3 includes a further bear¬ ing 31 which is intended to transmit thrust from the cup spring 19 to the lock plate 27 at low machine speeds and when the machine is stationary, this further bearing being located between the aforesaid two components and being centred on the lock plate by means of a hub 32. This solution is less refined than the solution afforded by the Figure 2 embodiment and also has the disadvantage that the bearing 31 is constantly subjected to pressure by the cup spring 19, to a greater or lesser extent.

Claims: Clai s 1. A rotary machine which comprises a housing (1) having a low-pressure side (2) and a high-pressure side (3) and working-fluid inlet and outlet channels (4, 5), a rotor (7) which is rotatably journalled in the housing and which during rotation is subjected to axial load by the working medium in a direction towards the low-pressure side (2) and towards thrust bearings (11) mounted in the housing, and is also subjected to axial load in a direction towards the high-pressure side (3) by a thrust balancing arrange¬ ment (15, 16) which comprises a piston-cylinder device and which under the influence of pressure fluid contingent on the operating conditions of the machine partially relieves the load on the thrust bearings (11) through the medium of an auxiliary bearing (17) which is arranged for limited movement against the action of an axially acting spring means (19) which is dimensioned to hold the rotor (7) urged towards the low-pressure side (2) when the thrust balancing arrangement (15, 16) is substantially inactive when starting and stopping the machine, characterized in that the auxiliary thrust bearing (17) is mounted on an outermost part of a rotor journal shaft (8) on the high- pressure side (3) of the rotor, between, on the one hand, a locking device (27) which is intended to lock the auxil¬ iary thrust bearing (17) and which is detachably mounted on the journal shaft, and the thrust balancing arrangement on the other; and in that the thrust balancing arrangement is located axially inwards of the auxiliary thrust bearing and has the form of two annular parts (15, 16) which are axially expandable in a known manner in a cylindrical re¬ cess (14) in the housing (1). 2. A rotary machine according to claim 1, characterized in that the auxiliary thrust bearing (30 Figure 3) is a roller bearing which has an inner ring which is secured on the journal shaft (8) by means of the locking device (27), and an outer ring which is located between the thrust balancing arrangement (15, 16) and the spring means (19) via the outer ring of a further roller bearing (31) having an inner ring mounted on the journal shaft (8), said bearing being intended for the transfer of an axial force between the spring means (19) and the journal shaft (8). 3. A rotary machine according to claim 1, characterized in that the auxiliary thrust bearing is a ball-bearing (17) of the kind capable of taking-up axial forces in both directions and having an inner ring which is secured on the journal shaft (8) by means of the locking device (27), and an outer ring which is located between the thrust balancing arrangement (15, 16) and the spring means (19). 4. A rotary machine according to any of claims 1-3, characterized in that the annular piston-cylinder device of the thrust balancing arrangement (15, 16) incorporates a radial chamber (21) for accommodating pressure fluid; in that the chamber (21) is located between two annular sealing devices (23, 24) which are arranged on the balanc- ing arrangement and which sealingly abut the cylindrical recess (14) in the housing; and in that a pressure fluid channel (22) provided in the housing (1) discharges into the cylindrical recess (14) at a location opposite the radial chamber (21) incorporated in the thrust balancing arrangement.

Inventors: SOEDERLUND FRITS, SOEDERLUND, FRITS
Applicants: SVENSKA ROTOR MASKINER AB
Application year: 1988
Main classification: F16C39
IPC codes: F01C21, F04C29, F16C19, F16C39