Patent Document

FIELD OF THE INVENTION 
     This invention relates to the field of vacuum pumps, in particular reducing the maintenance burden relating to dry vacuum pumps. 
     BACKGROUND OF THE INVENTION 
     Such vacuum pumps can be used to evacuate a process chamber, through which hazardous/aggressive process gases may be passed to perform various functions in use. Dry vacuum pumps typically comprise one or more oil filled gear boxes. These are generally located remotely from the pump swept volume within the pumping apparatus. The swept volume accommodates the pumping mechanism which, in turn, is attached to and driven by the gear box, via one or more rotating shafts. It is important to prevent the transfer of oil from the gear box to the swept volume as oil would contaminate the process gases and potentially migrate to the process chamber, causing damage to the article being processed. It is also important to prevent particulate matter from the swept volume from reaching the gear box as this may cause contamination of the gear box oil and, consequently, reduce the reliability of the gear box components. 
     Conventionally, rotary seals are used around the rotating shafts to prevent transfer of oil from the gear box. However, it is very difficult to produce rotary seals which are suitably reliable and hardwearing. In trying to achieve these goals, exceptionally complex and expensive seals have conventionally been developed. 
     Loss of oil from the gear box not only causes potential contamination, but leads to degradation of the gear box itself if the volume of oil is significantly reduced. One conventional system collects such migrating oil but regular maintenance must be carried out to replenish the levels in the gear box and to empty the oil collection chambers. 
     It is an aim of the present invention to increase the maintenance interval by providing a system that prevents or significantly reduces the loss of oil from the pump. 
     SUMMARY OF THE INVENTION 
     According to the present invention there is provided a vacuum pump comprising:
         a pumping mechanism;   a drive shaft for driving the pumping mechanism;   a gear box connected to the drive shaft for rotating the drive shaft; and   pressure control means defining a path to allow fluid to flow from the pumping mechanism to the gear box to reduce the pressure difference therebetween, and, located in said path, a reservoir for collecting oil passing along the drive shaft from the gear box towards the pumping mechanism so that, in use pressurised fluid flowing from the pumping mechanism towards the gear box urges oil collected in the reservoir towards the gear box.       

     By using the standard pressure cycle of the vacuum pump any oil collecting in the oil reservoir is regularly returned to the gear box such that the level of oil in the sump of the gear box is not significantly depleted over time. 
     The pressure control means may comprise one or more restrictions cooperating with the rotating shaft. These restrictions may define one or more chambers located along the length of the shaft. A first chamber may be proximate the pumping mechanism and a second chamber may be proximate the gear box. 
     The pressure control means may define a second path to allow fluid to flow from the gear box to the pumping mechanism to reduce the pressure difference therebetween. This second path may be defined, in part, by a bore within the drive shaft, the bore may have a fluid inlet proximate the gear box and a fluid outlet proximate a said chamber. 
     A non-return valve may be positioned in the first path between the oil reservoir and the gear box, the valve being arranged to be opened by pressurised fluid flowing from the pumping mechanism towards the gear box. This non-return valve may be activated by a pressure difference of 10 to 30 mbar. Such a sensitive valve ensures that each time the pressure rises (even minimally) in the swept volume in relation to the gear box, any collected oil will be returned to the sump. Preferably, the valve has an inlet connected to the reservoir and an outlet connected to a conduit for conveying oil towards the gear box, preferably to an oil sump. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       An example of the present invention will now be described with reference to the accompanying Figures in which; 
         FIG. 1  illustrates a schematic representation of a vacuum pump; 
         FIG. 2  illustrates a cross-section of a pump according to the present invention; 
         FIG. 2   a  shows an enlarged view of a restriction in  FIG. 2 ; 
         FIG. 3  illustrates a cross-section of a second pump according to the present invention; 
         FIG. 4  illustrates a pump of  FIG. 2  in use when the gear box pressure is higher than that of the swept volume; and 
         FIG. 5  illustrates a pump of  FIG. 2  in use when the swept volume pressure is higher than that of the gear box. 
     
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     A basic representation of a vertical cross section of a vacuum pump  1  can be seen in  FIG. 1 . A housing component  2  is provided which defines two primary internal cavities  3 ,  4 . The first of these defines the swept volume  3  of the pumping mechanism of the pump, the rotor  6  of the pumping mechanism being located within the swept volume  3 . The swept volume  3  has an inlet and an outlet (not shown) to allow the passage of process gases in use. The rotor  6  is mounted on a drive shaft  5  which rotates in use. The drive shaft  5  is coupled to a second drive shaft (not shown) by gears in the gear box  4  such that the two shafts rotate in synchronisation, allowing the rotors  6  mounted on the shafts  5  to intermesh and perform the pumping function. In order to try to maintain an oil free swept volume  3 , sealing mechanisms are generally implemented along the shaft in region  7  between the swept volume  3  and the gear box  4  to prevent migration of oil to the swept volume  3  from gear box  4 . 
       FIG. 2  shows a more detailed schematic view of a section of a pump according to the present invention. Within region  7 , pressure control elements  11 ,  12  and  13  are provided along the length of part of the drive shaft  5 . In this example, the pressure control elements are restrictions formed as part of the housing component  2  to provide a close but generally non-contacting tolerance with shaft  5 . These restrictions may alternatively be configured as illustrated in  FIG. 2   a , in which a resilient component  23  is fixed to the stationary housing thus forming a potentially contacting barrier between the housing  2  and the rotating shaft  5 . Where the pressure is raised sufficiently in chamber  15 , located between restrictions  12  and  13 , the component  23  may deflect allowing gas to pass from chamber  15  to the gearbox  4 . If, however the pressure is raised on the gear box side of component  23  the component will be deflected such that it is forced into contact with the shaft  5  such that the seal is enhanced and gas cannot pass from the gearbox  4  past restriction  13  to chamber  15 . 
     In typical use of a vacuum pump, the ambient pressure in swept volume  3  will vary between high values (potentially up to atmospheric) and very low pressures, as may be found in high vacuum conditions. In normal usage, the different areas of the pump will be pressure balanced such that all of the components will be maintained at high vacuum conditions. In this way, the chances of regions of higher pressure fluid seeping to areas of low pressure are minimised such that high vacuum conditions are not inhibited. Consequently, it is necessary to reduce the pressure in the gear box  4  in line with the pressures experienced in the swept volume  3 . This is achieved by providing free flow paths between the gear box  4  and the swept volume  3 . 
     The shaft  5  is provided with a central bore  19   a  which extends from the end of the shaft that lies within the gear box  4  to beyond the first restriction  13  as illustrated in  FIG. 2 . Radial passages  19   b  extend from this central bore  19   a  to the chamber  15  between restrictions  12  and  13 . A filter  16  is provided on the end of the shaft to prevent (or at least minimise the amount of) oil from passing from the gear box  4  towards the swept volume  3 . A further conduit  18 ,  27  is provided from the chamber  14  between restrictions  11  and  12  to the swept volume  3 . Conduit  18 ,  27  comprises a filter  17  which removes particulate matter from process gases passing from the swept volume  3  towards the gear box  4 . A third conduit  20  connects the chamber  14  with the gear box  4  via a non-return valve  21 . 
     Where the process gas does not comprise particles or other contaminants, filter  17  and conduit  18 ,  27  may be omitted from the device as shown in  FIG. 3 . Optionally, restriction  11  may be omitted too, in this example, however it is configured to permit passage of gas in either direction. 
     In use, and assuming that the entire pump  1  is initially at atmospheric pressure, the pressure will drop first in the swept volume  3  as this becomes evacuated. With reference to  FIG. 4 , since restriction  13  inhibits fluid flow and the pressure gradient acting across the non return valve  21  will tend to oppose its opening so that valve  21  remains closed, the path of least resistance for the higher pressure gas within gear box  4  will be through filter  16  and central bore  19   a  and radial passages  19   b . Filter  16  acts to remove any oil droplets which may otherwise be transported by the gas travelling from the high pressure region to the lower pressure region. This gas then enters chamber  15 , where restriction  12  allows the gas to pass to chamber  14  and from there through conduit  18  and in to swept volume  3  via filter  17  and conduit  27 . As shown in  FIG. 4 , the restrictions  11  to  13  define a first flow path (indicated by arrows  30 ) from gear box  4  to the swept volume  3 . Restriction  11  may also allow some transmission of this gas from chamber  14  to the swept volume  3 . Thus the pressure throughout the pump can be equalised. 
     The reverse process occurs (see  FIG. 5 ) when the swept volume  3  increases in pressure in relation to the gear box  4 , for example during a load lock pump down when the chamber being evacuated will initially return to higher pressures. Higher pressure gas from the swept volume  3  flows to the gear box  4  through the path of least resistance, that is, via filter  17 , as restriction  11  is configured to inhibit flow from the swept volume  3  to chamber  14  when conduit  18 ,  27  is present. This filter  17  prevents particulate contaminants from the process gas reaching conduit  18  and subsequently to chamber  14 . Such particulate materials would contaminate the oil and make it unsuitable for use in the gear box  4 . Restriction  12  then provides an adverse pressure gradient to the gas such that the path of least resistance for the gas is through non-return valve  21  and conduit  20  which feeds directly in to the gear box  4  above the level of the oil in the sump (not illustrated). As shown in  FIG. 5 , the restrictions define a second flow path (indicated by arrows  40 ) from the swept volume  3  to the gear box  4 . Minimal amounts of fluid may pass through conduits  19  and filter  16  (indicated by arrows  41 ). Through this mechanism, pressure can be equalised throughout the pump  1 . 
     During use, oil collects under gravity in reservoir  22  beneath chamber  14 . The oil in reservoir  22  is present due to, for example, imperfect sealing at restrictions  12  and  13  and any oil mist that may pass through filter  16  from the gear box  4 . 
     As described above, during the pressure equalisation process where the gear box  4  is brought up to the same pressure as the remainder of the pump, relatively higher pressure gases will thus pass through reservoir  22  and activate non-return valve  21 . Non-return valve  21  is preferably sensitive and so does not require a high fluctuation/difference in pressure to be opened, typically a pressure difference of 10 to 30 mbar will be sufficient to open the valve. Once opened, oil may be returned to the main sump of gear box  4 . In practice, this oil return process will occur each time the pressure in the swept volume  3  is greater than that found in the gear box  4 . Thus any oil that does leak along the shaft  5  will, automatically, be returned to the sump in the gear box  4 , rather than having to be periodically drained from reservoir  22 . 
     Since the inventory of oil is retained in this way the requirement for maintenance to replenish the oil in the gear box  4  or to empty any reservoirs is significantly reduced. 
     In the example where restriction  11 , filter  17  and conduit  18 ,  27  are not required, the chamber  14  may be combined with the swept volume  3  such that any oil being transmitted as far as the pumping mechanism  6  is removed during the next pressure fluctuation cycle. In this case, the non-return valve  21  and oil reservoir  22  could be located at the base of the swept volume  3  formed within the housing  2 , and so any oil that may pass through to the swept volume  3  is collected by gravity in the reservoir  22  and subsequently returned to the gear box  4 . Preferably, however, (as illustrated in  FIG. 3 ) restriction  11  is retained to provide an additional barrier to oil trying to pass into the swept volume  3 . In this configuration, the oil collection point, reservoir  22  is located remotely from the swept volume so that the presence of oil therein may be minimised.

Technology Category: 2