BACKGROUND OF THE INVENTION
1. Technical Field
The present invention relates to a multiple segment lobe pump with reduced or zero pulsations in the outflow.
2. Related Background Art
The first lobe (air) pump was invented in 1854 by a couple of wood mill owners in Connersville, Ind. named Francis and Philander Roots and became known as ‘The Roots Blower’. The design featured two side-by-side rotors that were each shaped sort of like a two dimensional hourglass. As the rotors turned, each delivered a ‘puff’ of air, twice per revolution. The blower was intended to produce the intermittent volume of airflow for uses in their mill. In the early 1900's, engineers at the Howard Pump Company in Eastbourne, England realized that if the blower were to run at a relatively low speed, it could forcibly transport a volume of incompressible media, such as liquids or semi-solids, between two locations. With that discovery, the first lobe (transfer) pump was born.
Up until the early nineteen-seventies, the pumping mechanism of the lobe pump consisted of two parallel shafts, each fitted with a single rotor that had multiple lobes with a profile that was parallel to the axis of rotation of the respective shaft. In other words, the lobes were straight sided. Depending on the application, the number of mating lobes was usually two or three and in some cases four. However, such pumps produce flow pulsations that are undesirable in many applications and as a result, have limited their wide spread use. By its design a lobe pump is a positive displacement pump. It is capable of pumping a wide variety of liquids, gels and granular materials. Current lobe pump applications include the transport of polymers, paper coatings, surfactants, paints, adhesives and a large variety of food applications such as; berries, fruits, chopped vegetables, cereals, grains and many other food products.
Starting in the mid-1970's with the advances in machining methods, the helical lobe pump was developed. The curved nesting lobe design significantly reduced the magnitude of the pulses but did not eliminate the non-continuous pump flow characteristic. In recent years, several manufacturers realized that a continuous flow, pulsation free helical lobe is possible by increasing the ‘pumping chamber isolation region’ so as to include the extent of the helical wrap of each lobe.
Currently, four and five helical lobe, non-pulsating pumps are available from several manufacturers. In order for these pumps to be pulsation free, the housing design must provide a ‘pump chamber isolation region’ (PCIR) that spans the separation angle between the lobes plus the helical wrap angle. In the case of a four lobe design, the angular lobe separation angle is 90° and the helical wrap angle must be 90° requiring a PCIR of 180°. The distance between the two sealing arcs is, by physical geometry equal to the center distance between the two shafts. The inlet and discharge flow area is therefore equal to the rotor height times the distance between the two shaft centers.
A three helical lobe, non-pulsating pump is currently not manufactured because of the geometric limitations related to the PCIR. A three-lobe design has a lobe separation angle of 120°. Adding the wrap angle required to seal a volume of flow within the pumping cavity and provide continuous pulse free flow, requires a PCIR of 240° resulting in an unworkably small inlet and discharge opening.
There is a need for designs of straight lobe pumps with reduced pulsation in the outflow. There is a need for helical lobe pumps that provide wider inlet and outlets on the pump housing. There is a need for a design that enables two and three lobe helical lobe pumps. There is a need for lobe pump designs that allow flexibility in choosing the size of the pumping chamber and the inlet and outlet dimensions of the pump. There is a need for a pump that retains all of the desirable features of a single segment lobe pump, which include the ability to handle viscous fluids, mixed media (liquid and solid) and semi-solids while providing continuous, low pulsation or pulsation-free flow.
DISCLOSURE OF THE INVENTION
The invention is directed to a means of eliminating the flow pulsations in the flow of the lobe pump in order to generate a steady, continuous discharge flow. One embodiment incorporates two or more co-axial pump segments on each drive shaft. Each pump segment on the shaft is identical to the adjacent segment and is an independent, full function pump device. Each of the segments of the multi-segment lobe pump runs in parallel, each producing the same flow. As such, there is no fluid dynamic similarity to a ‘staged’ rotor-dynamic pump that may have multiple rotors on the same shaft that run in ‘series’ in order to generate an increase the hydrostatic pressure. Embodiments include two, three and more lobes per rotor in combination with two, three and more segments.
The individual pumps are positioned with a predetermined angular offset with respect to the lobes in each succeeding segment. Since the flow of each segment is additive, the timing of the segments eliminates the cyclic variation in the total flow resulting in smooth, continuous discharge flow. In one embodiment a three straight-sided lobe pump configuration with five pump segments per shaft, reduces the flow pulsations at both the inlet and discharge to less than one-percent of the total flow.
In another embodiment, timing gears set the angular position of each rotor. In one embodiment a first shaft is driven by an outside source and the second shaft is precisely driven relative to the first shaft. In addition, the timing gears position the individual rotors very precisely so that the individual rotors within a segment never touch.
In another embodiment multiple lobe, multiple segment pumps are made using helical lobe rotors.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 shows the exterior elements of a pump.
FIG. 2 is a cross sectional view of a two lobe single segment pump as known in the art.
FIG. 3 is a second cross-sectional view of a two lobe single segment pump as known in the art.
FIG. 4 is a view of a pair of two lobe rotors.
FIG. 5 is a cross-sectional view of a two lobe pump as shown in FIG. 3 with additional angular indicia.
FIG. 6 shows graphs of the outflow from two lobe single segment pumps equivalent to that shown in FIG. 5.
FIG. 7 is a view of the rotors for a two segment two lobe pump embodiment of the present invention.
FIG. 8 is a cross sectional view of a two segment two lobe pump embodiment.
FIG. 9 is a second cross-sectional view of a two segment two lobe pump embodiment.
FIG. 10 is a chart of the outflow of a two segment two lobe pump embodiment.
FIG. 11 is a chart of the outflow of a three segment two lobe pump embodiment.
FIG. 12 shows the interior pump rotor assembly for a five segment three lobe pump.
FIG. 13 show the rotor for a four lobe pump including anti-friction plugs.
FIG. 14 is a perspective drawing of a helical three lobe pump rotor having a wrap angle of 120 degrees.
FIG. 15 is a cross-sectional view of a single segment helical three lobe pump showing issues with a pump chamber isolation region required to accommodate a helical three lobe pump with a 120 degree wrap angle in a single segment design.
FIG. 16A shows a side view of a three segment three helical lobe rotor.
FIG. 16B is a perspective view of the rotor of FIG. 16A.
FIG. 17 is a top view of the rotor of FIG. 16A.
FIG. 18 is a cross-sectional view of a three segment three lobe helical pump.
FIG. 19A is a perspective top view of a separator plate embodiment.
FIG. 19B is a perspective top view of a second embodiment of a separator plate.
FIG. 20 is a side view of a lobe pump using the separator plate embodiment of FIG. 19A.
FIG. 21 is a cross-sectional view of the lobe pump of FIG. 20.
FIG. 22 is an end view of a lobe pump using the separator plate embodiment of FIG. 19A.
FIG. 23 is a cross-sectional view of the lobe pump of FIG. 22.
MODES FOR CARRYING OUT THE INVENTION
To fully explain how the basic prior art lobe pump operates, and to help explain the instant invention by contrast, FIGS. 1-6 are included that show several views of a prior art lobe pump. It should be understood and apparent however that some components and descriptions are common to both the prior art pumps and embodiments of the current invention. As an example both the prior art and the current invention include housings, inlets, outlets and at least a pair of rotors. Descriptions specific to embodiments of the instant invention, for brevity, avoid repeatedly restating these common features. The pump has two side-by-side rotors, each with two identical sets of lobes. FIG. 1 illustrates the three primary exterior views of the machine. FIGS. 2-5 illustrate interior sections and components. FIG. 6 shows a measure of performance.
Referring now to FIG. 1 a typical exterior housing for pumps of both prior art design and the current invention is shown. Three views are shown in the figure: a side view 100, a second side view 101 and a top view 102. The pump is seen to include a housing 103, the housing including a base 104 and a top 105. In the instance shown the top 105 is seen to be bolted onto the main body of the housing 103. The housing further includes openings 106, 107 for inflow and outflow. Although typically designating one opening 106 for inflow and the other 107 for outflow it should be understood that the pump designs discussed below are symmetrical and either opening could be used for inflow or outflow or both if the pump is run in the reverse direction. The face 108 of a first rotor and the edge 110 of a second rotor can be seen through the opening 106. The housing further includes a passage 111 through which a drive or input shaft 109 protrudes. The pump is driven through rotation of the shaft 109 typical using a motor (not shown). The indicia AA and BB show lines through which cross sectional views of the pump are taken. The cross sectional views shown in FIGS. 2 and 3 respectively.
Referring now to FIG. 2, The AA cross section of the pump of FIG. 1 is shown. The pump is seen to be comprised of a housing 103 including an inlet 106 and an outlet 107. The interior of the pump is comprised of two lobe rotors 201 and 202 the rotors rotate in the directions 204 shown. Rotation of the individual rotors is through use of timing gears (not shown) attached to the shafts 206, 207. The rotors are likewise attached to the shafts 206, 207 and rotation of the shafts rotates the rotors. The pump chamber isolation region (PCIR) 203 is defined by the housing, rotor and the points 208, 209 where the rotor meets the housing. There is a symmetrically identical PCIR for the second rotor 202 bound by the line 210. The shafts and the rotors are positioned such that the simultaneous rotation of the rotors results in meshing of the rotors thereby causes a pumping action wherein a fluid enters a central portion of each lobe 211 at the inlet of the housing, passes through a pump chamber isolation region, and the fluid is displaced from each lobe at the outlet by the bulbous end 212 of the second lobe. Thereby resulting in a positive displacement pumping action. Although defined as a region, the PCIR is measured by the angle 205. In the example shown the PCIR would be quantitatively described as 180°. In a straight walled, conventional, lobe pump the PCIR is equal to the angle between the lobes of the rotor. In the case shown the angle between the lobes for a two lobe rotor is 180°. Or more generally the angle between the lobes of a multiple lobe rotor is 360°/number of lobes. Thus a single segment lobe pump made with a three lobe rotor would have a PCIR of 120°.
Referring now to FIG. 3, further components of the lobe pump are seen in this cross section along the line BB of FIG. 1. The pump is seen to comprise dual rotating shafts 301, 310. A first shaft 301 is the power input shaft, which is driven by an electric motor or other means. Power is transmitted to the second shaft 310 by means of timing gears 302 which are rigidly affixed to each shaft. Rotors 305, 306 are concentric with and rigidly affixed to their respective shafts 301, 310. The rotors are cross hatched and shown parallel to one another in the same position as seen in FIG. 2. Each shaft is positioned and held in place by ball bearings: an upper bearing 303 and a lower bearing 309. In order to prevent fluid from entering the region of the bearings, mechanical shaft seals 304, 308 are mounted in the housing 312. An additional seal 311 is seen at the top of the power input shaft 301. Each rotor is precisely machined so that when they are mounted in their respective bearings and positioned by the timing gears, a very close, uniform clearance is established between the two rotors as well as each rotor and the wall of the housing. There is no metal to metal or rotor to metal or rotor to rotor contact between components. The PCIR 307 is also shown. All components are contained within the sealed housing 312. In a preferred embodiment for every full 360° rotation of the drive shaft 301, each rotor also rotates 360° thereby delivering four discrete volumes from the two pump chamber isolation regions of liquid per revolution into the inlet side and discharge out the outlet side of the pump. In other embodiments there is additional gearing between the input shaft 301 and the shafts 310 that drive the rotors such that a full rotation of the input shaft may result in more or less than a full rotation of the shafts 310. Pumps that are made using different number of lobes would deliver correspondingly different numbers of volumes from the PCIR. As an example an equivalent three lobe pump would deliver 6 volumes per rotation.
The isolated lobe rotors are shown in FIG. 4. The rotors 401, 402 are each seen to be mounted on shafts 403, 404. The point of nearest approach 405 of the rotors is maintained as nearly fluid tight by machining and precise movement of the rotors relative to one another by the timing gears, not shown. The timing gears would mount on the shafts at the approximate locations 403, 404 shown. The rotors shown are termed straight wall or conventional rotors as the sides of the rotors as shown are vertical and the point where the meet 407 is a straight line. The rotors 401, 402 in this embodiment are identical. This is in contrast to helical rotors, discussed later, where the rotors are twisted into a helical shape and the paired rotors are mirror images of one another.
Referring now to FIG. 5 an index 505 is shown that is used in subsequent examples to discuss the outflow performance of the pumps. The index measure the angle of rotation of the input shaft and the rotors. A complete pumping cycle is defined as 360° rotation of the index shown. Each rotor would deliver two PCIR volumes for every 360° rotation. The PCIR being defined as the region isolated between the rotor 508 and the housing 501. The outer points 506, 507 define the boundaries of the PCIR. The flow is characterized in that for every 360 degrees of the index, four PCIR volumes would enter 502 and four PCIR volumes would exit 503. It should be noted the pumps are symmetrical and could also be run in reverse thereby reversing the flow.
Referring now to FIG. 6, four graphs of the output of the dual lobe pump described and illustrated thus far is shown. The horizontal X-axis is the index as described in FIG. 5 and ranges from 0° at the left to 360° at the right. The vertical axis in each graph represents flow out from the pump. The top graph 601 show the flow due to the first rotor. The next graph 602 shows the flow from the second rotor. The third graph 603, shows the two flows superimposed and the fourth graph 604 shows the flows summed and represents the total flow out of the pump. The problem with pulsation of conventional lobe pumps is readily apparent where the peak to valley variation 605 is about 25%.
Multiple Segment Pumps
The rotors for a multiple segment lobe pump embodiment of the present invention are shown in FIG. 7. The pump is comprised of the housing and other attributes already discussed. The pump is further comprised of four rotors 704, 705, 705, 707 the rotors are contained in two separate segments 701 and 702 the segments are separated by a separator plate 703. The separation plate is in place between each set of nested rotors in order to isolate the pump segments from each other. The plate 703 is floating between the rotors and perpendicular to the rotating shafts 708, 709. It is positioned by a close fit with between the semi-circular ends and the opposing semi-circular recesses in the pump housing. The plate also has dual circular openings that allow the shaft and a circular hub portion of each rotor to pass through. The openings are not visible in the figure since they are hidden under the lobe rotor elements. The dual openings fit in close proximity to the circular hub to minimize transverse leakage between the segments. Each segment act as an additional lobe pump made up of dual nesting rotors and a seal plate to prevent flow between the segments.
The rotors are fixed to rotating shafts 708, 709. The rotors 704, 706 are affixed to the same shaft 708 and the rotors 705, 707 are fixed to the same shaft 709. The rotors attached to the same shaft are offset by an index angle described in FIG. 8. In the example shown the in FIG. 7 the index angle between rotor 704 and rotor 706 is set at 90 degrees. The same is true of the index angle between the other set: rotor 705 and rotor 707. The rotation of the separate shafts is synchronized through use of timing gears attached to the shafts 708, 709.
A cross-sectional view of a two segment lobe pump utilizing the rotor assembly shown in FIG. 7 is seen in FIG. 8. The pump is comprised of a housing 801 having an inlet 802 and an outlet 803. Located within the housing are two pump segments each using two lobe rotors. The rotors are located on either side of a separation plate not seen here but shown in FIG. 7. The rotors 804 and 805 on a first side of the separation plate and the rotors 806, 807 are on a second side of the separation plate. The rotors are separate segments are fixed relative to one another and displaced by the index angle 809. In the case shown the index angle is 90°. In a preferred embodiment the index angle for a multi-segment straight sided lobe pump is equal to the angular separation between the lobes divided by the number of segments. In the instant case, the angular separation between the lobes is 180°. There are two segments and therefore this preferred case has an index angle between the lobes on separate layers of 180/2 or 90°.
An additional view of a two segment lobe pump discussed in FIGS. 7 and 8 is shown in FIG. 9. The pump is comprised of a housing 901 which encases a first segment comprised of lobe rotors 902, 903 and a second segment comprised of rotors 904, 905. The segments are separated by a separation plate 911. The Rotors are fixedly attached to shafts 906, 907. The first shaft 906 extends beyond the housing and acts as an input shaft to power the pump. The second shaft 907 is encased within the housing. The rotation of the shafts is synchronized through use of timing gears 908 attached to each shaft such that upon rotation of the input shaft the second shaft 907 is rotated in a precise synchronization with the first shaft. The precise synchronization is required to synchronize the motion of the first lobe rotor 902 with the motion of the second lobe rotor 903 both located in the first segment as well as to synchronize the motion of the third lobe rotor 904 with motion of the fourth lobe rotor 905 both located in the second segment. These timing gears set the angular position of each rotor with one shaft driving and the other shaft is driven. In addition, the gears position the individual rotors very precisely so that they never actually touch. The pump further includes seals 909 to prevent leakage into the bearings and bearings 910 to hold the shafts in place. The inlet and exit ports of the pump are not visible in this view.
The outflow performance of the two segment dual lobe pump is shown in FIG. 10. The individual segments perform as individual pumps with negligible leakage between segments. The output of the multiple segment pump is therefore the sum of the output of each segment. The effect on inlet and discharge pulsation of the dual segment, dual lobe pump is shown in the upper plot 1003 that represents the summation of the instantaneous area change of the indexed segments added together. The flow of individual segments are shown in the lower curves 1001, 1002. As the instantaneous area curve indicates, there is only about a 5% variation in instantaneous area compared to the 25% variation with a single segment pump as shown previously in FIG. 6.
Outflow performance can be improved more with the addition of segments. In each case the total flow is the sum of the flow from each segment. The index angle between the lobes on different segments is set to equal the angle between the individual rotor lobes divided by the number of segments. In the case shown in the FIGS. 7, 8 and 9 a two segment dual lobe pump has a 180 degree angular separation between lobes on an individual rotor and the lobes on adjacent layers in a two segment are indexed by 90°. In the case of a three segment, dual lobe pump with two lobes per individual rotor, the segments would be indexed sixty degrees from each other. If there were four pump segments, the index angle of the segments on each shaft would equal forty-five degrees, etc.
The addition of another pump segment to create a three segment dual lobe pump would have a flow variation of 3.9%. Performance of such a pump is shown in FIG. 11 the bottom curves 1101, 1102, 1103 show the outflow (y axis) as a function of angular rotation (x axis) for each segment. The top curve shows the output of the pump as the summation of these three lower curves. Similarly a four segment pump version would have a flow variation of 2.1%.
The invention is not limited to two lobe pumps. Embodiments include three four and more lobes on the individual rotors. The same design principals already discussed apply. A three lobe pump would have a 120 degree separation between lobes. The pump chamber isolation region for straight wall lobes would be 120 degrees. The same as the angular separation of individual rotors. In a two segment three lobe pump the rotors on adjacent levels would be indexed by 60°. That is as already described the rotors on adjacent levels are indexed by the angle between lobes divided by the number of segments or 120/2=60°. Analysis of the flow profiles equivalently to what has been shown indicates that a three lobe, two segment pump can reduce the pulsation effect of the single segment pump from 35.1% to 10.0% while a three segment, three lobe rotor geometry will reduce the pulsation intensity from 35.1% to 5.2%. A five segment, three lobe pump, shown in FIG. 12, will reduce the intensity of pulsation down to less than 1%.
Referring to FIG. 12, the components of a pump having both a plurality of lobes on each rotor and a plurality of segments are shown. Such a pump would have features in common with those already discussed such as a housing and inlet and outlet ports. In the embodiment shown there are two three-lobe rotors in each segment. A first, top, segment 1201 is seen to be comprised of two rotors 1206, 1207. Similarly the other segments 1202, 1203, 1204, 1205 each also contain a pair of rotors. The segments are separated by separation plates 1208. The rotors are mounted on shafts 1209 that when rotated cause the rotors to also rotate. Attached to the shafts are timing gears 1210, 1211 that synchronize the relative motion of the two rotors such that the lobes mesh during rotation and form a close but non-contact seal between the two lobes on the same segment but different shafts. In this case the rotors on the second segment 1202 from the top segment 1201 are indexed relative to the rotors on the top by 24 degrees. This is, as already discussed, the angle between the lobes of an individual rotor divided by the number of segments. Here that is 120° divided by 5 segments or 24° indexing of rotors between adjacent levels.
Similarly, four lobe multi-segment pumps can also be constructed. A four lobe, four segment pump geometry would reduce the pulsation intensity from a one segment intensity of 13.6% down to 0.20%. A rotor 1301 for a four lobe pump is shown in FIG. 13. The rotor is comprised of four individual lobes, two of which 1302, 1303 are numbered in the Figure. The individual lobes also include plugs 1305 positioned in holes 1304 drilled in each of the lobes. The plugs are anti-friction plugs made of a material that will glide easily over the separation plates between segments. The plugs may be made of metal, plastic or be roller bearings. In a preferred embodiment the plugs are made of Teflon® (Teflon is a registered trademark of E. I. Dupont De Nemours and Company a Delaware corporation).
The exposed plug is fitted to have a slight contact with each separation plate in order to provide stability and eliminate plate vibration. The plugs although shown in a four lobe rotor likewise are usable on rotors with any number of lobes. The plugs fitted in holes drilled in the top and bottom surfaces of the lobe rotors, glide over and lightly contact the separation plates when the lobe rotors rotate.
Helical Lobe Pumps
Starting in the mid-1970's with the advances in machining methods, the helical lobe pump was developed. The curved nesting lobe design, comprising a pair of helical lobes that are mirror images of one another, significantly reduced the magnitude of the pulses but did not eliminate the non-continuous pump flow characteristic. In recent years, several manufacturers realized that a continuous flow, pulsation free helical lobe is possible by increasing the ‘pumping chamber isolation region’ so as to include the extent of the helical wrap of each lobe.
Currently, four and five helical lobe, non-pulsating pumps are available from several manufacturers. In order for these pumps to be pulsation free, the housing design must provide a ‘pump chamber isolation region’ (PCIR) that spans the separation angle between the lobes plus the helical wrap angle. In the case of a four lobe design, the angular lobe separation angle is 90° and the helical wrap angle must be 90° requiring a PCIR of 180°. The distance between the two sealing arcs is, by physical geometry equal to the center distance between the two shafts. The inlet and discharge flow area is therefore equal to the rotor height times the distance between the two shaft centers.
A three helical lobe, non-pulsating pump is currently not manufactured because of the geometric limitations related to the PCIR. A three lobe design has a lobe separation angle of 120°. Adding the wrap angle required to seal a volume of flow within the pumping cavity and provide continuous pulse free flow, requires a PCIR of 240° resulting in an unworkably small inlet and discharge opening.
Referring to FIG. 14 a three lobe helical rotor 1401 having a wrap angle of 120 degrees is shown. The rotor is comprised of three lobes 1402, 1403, 1404 the lobes are symmetrically placed around the center 1407 of the rotor. The center includes a hole 1407, in this embodiment that is slotted, to receive a shaft to drive the rotor. The rotor is twisted into a helix such that the bottom 1405 point of each rotor is angularly displaced from the top. In the instance shown the point 1408 on the bottom of the lobe 1404 is displaced by 120 degrees from the equivalent point 1406 on the top edge of the lobe 1404. The wrap angle is better shown in the end view of FIG. 17. When used as mirror image pairs in a lobe pump, a helical rotor can provide continuous pulse free flow. The modification from the straight walled lobe rotors is that the pump chamber isolation region must be expanded to account for the wrap of the rotor. For a helical lobe pump the pump chamber isolation region is the separation angle of the lobes plus the wrap angle of the helical rotor. In the case of a single segment three lobe rotor with a 120 degree wrap angle the pump chamber isolation region must equal 240 degrees resulting in very small unworkable inlet and outlet ports. This issue is demonstrated in the cross-sectional view of FIG. 15.
Referring to FIG. 15 the lobe pump includes many features that have already been discussed in conjunction with non helical lobe pumps. The pump is comprised of a housing 1502 which encloses a pair of rotors 1502, 1503. The rotors in this case are helical and are mirror images of one another, but this attribute is not visible in a cross-sectional view. The rotors are each mounted on shafts 1507 that rotate driving the rotors in the direction shown, for flow in the direction shown. The flow is reversed if the rotation is reversed. The pump further includes an inlet 1504 and an outlet 1505. The pump chamber isolation region 1508 is seen to span an angle 1509 of 240 degrees. This results in constrictions 1506 and that inlet and outlet of the pump. It is because of this geometric constraint that three lobe helical pumps are not commercially available. The solution is the instant invention of a multi segment pump.
Referring now to FIGS. 16A and 16B, two views of a rotor assembly 1601 for a three segment helical three lobe pump is shown. In effect the helical rotor with a 120 degree wrap angle, required for continuous flow from the pump, has been cut into three equal segments. The assembly includes three helical rotors 1602, 1603, 1604 with each rotor having a wrap angle of 40 degrees. The rotors are mounted to a shaft 1605. The mounting is such to include spacing 1606 between the rotors to accommodate a separation plate in the final pump assembly. The rotors are seen to be offset or indexed from one another. The index angle between neighboring rotors being the same as for a conventional lobe pump or the angle between the lobes of the rotors divided by the number of segments. In the case shown for a three lobe pump the index angle is 120/3 or 40°.
An end view of the same rotor assembly is shown in FIG. 17. The assembly is seen to be comprised of three helical lobe rotors the wrap angle is the angular displacement of equivalent points on the top and bottom face of a rotor or in the instance shown the equivalent points 1705, 1706 at the outer tip of the rotor 1702 are rotationally displaced by a wrap angle 1707 of 40°. Adjacent rotors are rotationally indexed from one another by the index angle 1710. That is the points 1709 on the middle rotor 1703 is rotationally displaced from the point 1708 on the top rotor 1702 by the index angle 1710. In the embodiment shown the index angle 1710 is 40 degrees.
Referring now to FIG. 18, a cross-sectional view of a three segment, helical three lobe pump is shown. The pump 1801 is comprised of a housing 1802 that includes an entrance 1803 and an exit 1804. The housing encloses the two of the multiple rotor assemblies shown and discussed in FIG. 17. The rotors on each assembly are mirror images of their corresponding meshing rotor on the other assembly. Only the top two of the three segments are shown. The top rotor is cross hatched and the middle level shown in dashed lines. The pump is comprised of helical rotors 1805, 1806 in a first segment and rotors 1807, 1808 in a second segment. The rotors attached to the same drive shaft in adjacent segments are displaced from one another by the index angle 1810. The design shown is a three lobe three segment pump so that the index angle is 40°. The pump chamber isolation region 1811 is defined by its circumscribed angle 1809. In the instant case the PCIR angle is the angle between the lobes on a single rotor or 120 degrees plus the wrap angle of 40 degrees resulting in the PCIR angle 1809 of 160°. Note by contrast with the design shown and discussed in conjunction with FIG. 15, the multiple segment helical pump has PCIR angle of 160° rather than the 240° required with a single segment. The inlet 1803 and outlet 1804 are not constricted in the design of FIG. 18 as they were in the design of FIG. 17.
Although a design for a three segment three helical lobe pump was shown. From the discussion, generalization to any number of lobes, wrap angles and segments should be clear to those skilled in the art.
Helical Lobe Pumps and Stationary Separation Plate Design
The designs of the conventional lobe pumps discussed above have two, parallel rotating shafts each of which drive a pump member (rotor) that has a repetitive contour shape, called lobes that allows the two rotors to precisely nest with each other along a plane that is perpendicular the axis of rotation of each rotor. A gear mounted on each shaft drives each shaft in a counter-rotating manner. The invented lobe pumps include a plurality of stacked pairs of lobe rotors within the same housing. The rotors attached to the same shaft are sequentially or offset by an offset angle that is dependent upon the number of lobes and the number of pairs of lobes as already discussed. In order to isolate the pairs of lobe rotors located within a layer, a flow separation plate is installed between each set to prevent cross-flow between the stacked rotors. The separation plates discussed thus far (see for example 1208 in FIG. 12) are floating between the lobe rotors 1206. In another embodiment plugs (1305 in FIG. 13) are placed in the rotors to prevent wear of the rotors and contamination as the rotors rotate on the separation plates.
Now, in another embodiment shown in FIGS. 19A-23 pump designs, the segment separation plates are shown in a fixed position relative to the pump housing thereby making a design where the segment separation plates can be precisely located relative to the rotor shaft assemblies which are positioned relative to the pump housing by the fixed position of the ball and/or roller bearings.
Referring to FIG. 19A, the separator plate is comprised of a flat plate 1901 having a top surface 1912 and a bottom surface 1908 and matching semi-circular ends 1904 and 1905. The semi-circular ends having internal surfaces 1906, 1907 and external surfaces 1917, 1918. The side edges 1911 of the plate are tangent to the semi-circular ends. Two holes, 1902, 1903 are located equidistant from the horizontal center 1910 of the plate 1901 to allow rotating elements of the pump (not shown) to pass through. The internal radius of curvature of the internal surfaces 1906,1907 are concentric with the pass through holes 1902 and 1903. The holes 1902, 1903 are sized to allow a small clearance between the stationary separation plate and the rotating pump member (not shown). The depth 1915 of the identical semi-circular ends 1904, 1905 between the top surfaces 1914 of the semicircular ends and the surface 1912 is established by the width of the respective rotor (not shown) that is positioned therein so that a small clearance exists between surface 1912 and the adjacent rotating pump member and similarly on the opposite side 1908 with the adjacent pump rotor thereof. The separator plate has a top surface 1912 and a parallel bottom surface 1908 (not visible but the opposite surface from 1912) and parallel side edges 1911. The radii of curvature 1916 of the external surfaces 1917, 1918 are in-line along a common axis 1919 with the centers of holes 1902 and 1903 and the centers for the radii of curvature 1916 are offset in a direction horizontally outward 1920. This external radius 1916 can be equal to or larger than the internal curvature of the surfaces 1906 and 1907. The outer surfaces 1917, 1918 of the semi-circular ends 1904, 1905 position the separation plate within the lobe pump housing (not shown) the same way as two close fitting dowel pins would do in two adjacent dowel holes. In this case, the outer surfaces 1917, 1918 limit both translational and rotational movement of the separator plate in the clearance between the separation plate and the adjacent internal surface(s) of the pump housing. In a multiple segment lobe pump where nested pairs of rotors are stacked such as seen in FIG. 12, this embodiment of the stacked pumps are installed into the pump housing so that the parallel surfaces 1914, 1908 fit directly against adjacent separator plate surfaces and are clamped together between mating surface of the pump housing on one end and the end cap on the other end as will be demonstrated in FIG. 23. In this way, the individual separator plates are precisely located relative to one another and relative to the rotor pairs of the pump. The opening 1909 between identical semicircular ends 1904, 1905 is equidistant from the theoretical horizontal centerline of plate element 1913 and is dimensionally set to at least hold and isolate the volume contained within the hollow region between two adjacent rotor lobes, straight or helical, and adjacent separator plates. The fixed separator plate eliminates the possibility of direct or incidental abrasive contact between the pump rotors and the separator plate.
In another embodiment shown in FIG. 19B, the separator plate includes semicircular ends 1904, 1905 that are positioned such that they extend both above and below the plate 1901. The separator shown in FIG. 19B functions the same as that in FIG. 19A and the other described elements of FIG. 19A are included in that of FIG. 19B. The separation plate of FIG. 19B further includes bottom surfaces 1921 on the semicircular ends 1904, 1905. The bottom surfaces 1921 are the same size, shape as and parallel to the top surfaces 1914 of the semicircular ends. When the pump is assembled the top surfaces 1914 are pressed against the bottom surfaces 1921 thereby fixing the distance between the flat plates 1901.
FIG. 20 shows an outer view of an assembled lobe pump. The pump is comprised of a housing 2001 that includes end covers 2002 that are, in the example shown bolted to the main part of the housing 2001. The pump is driven by a shaft 2003 that extends outside of the housing. The entrance 2006 of the pump is an opening through which the fluid being pumped enters the housing and is carried by the movement of the lobes as they rotate to the opposite side of the housing where a similar exit opening exists. The stacked lobes 2004 of the pump can be seen through the pump entrance 2006. There are four pairs of lobes 2004 in the example shown. The pairs of lobes are separated from one another by separator plates 2005. In the example three separator plates are used to separate four layers of lobes. In general there are n−1 separator plates for n lobes. The interior of the housing defines the pumping chamber for the bottom lobe. In another embodiment (not shown) an additional separator plate can be used beneath the bottom lobe to separate the lobe from the housing. The pump is shown in cross-section A-A 2007 in FIG. 21.
FIG. 21 shows a view 2101 of the A-A cross-section of FIG. 20 as well as a magnified view 2102 of the edge of the end piece of the separator plate and the pump housing 2103. The view is looking down upon a pair of lobe rotors 2104 in a layer of the lobe pump. The flow 2106 through the pump is right to left as the lobes rotate in the direction 2110 shown. The top edges of the end pieces 2107 of the separator plates 2105 are seen as they fit against the wall of the housing 2103. In the magnified view 2102 the housing 2107 and the separator plate end piece 2107 are separated by a gap 2111 that allows movement and therefore placement and removal of the stacked lobes and separator plates during assembly and disassembly. In another embodiment the gap 2111 is sealed thereby allowing pumping of very low viscosity and gaseous materials without leakage around the lobe rotor pumps. The plates are firmly held in position by the clamping action of the end covers of the housing once assembled. The shafts 2108 that drive the lobes rotors 2104 extend through holes in the flat plate of the separator plates 2105. The pumping region is defined by the arc 2109 that is determined by the number of individual lobes and the style of the lobe rotors (straight or helical) as discussed in previous Figures. In the case shown there are four lobes and the lobe rotors are straight edged, not helical.
FIG. 22 shows an end view of the same lobe pump as seen in FIGS. 20 and 21. The housing 2201 includes an end cover 2202. The end cover is bolts 2205 (only two of the plurality of bolts are labeled) hold the end cover to the housing. Once the housing is bolted into place the separator plates that further includes the end pieces as shown in FIGS. 19-21 are securely held in place. The Figure also shows the hole 2203 through which the drive shaft for the lobe rotors enters the pump housing. The B-B cross-section 2204 is shown in FIG. 23.
Referring now to FIG. 23, a lobe pump 2301 that includes four pairs of lobe rotors 2304 is shown. The lobe rotors 2304 are driven by the shaft 2302. The stacked layers of lobe rotor pairs are separated by separator plates 2305. The separator plates are as discussed in conjunction with FIG. 19 and include a flat plate, a pair of holes 2309 in the flat plate through which the drive shafts for the lobe rotors pass and vertical end pieces extending from the plat portions that fit against the wall 2303 of the housing for the pump. The separator plates are sized to fit against the wall 2303 of the pump. In one embodiment the fit is a friction fit. In another embodiment for pumping low viscosity fluids or gases there is a seal formed between the outer edges of the separator plates and the wall 2303. The separator plates 2305 are fit together in a stack with contact points on the top 2306 and bottom 2307 of each separator plate end piece. The end cover 2310 of the housing presses against the top surface 2311 of the topmost separator plate 2312 thereby holding the entire stack of separator plates 2305 in position. In the embodiment shown there are n−1 separator plates (in this case 3) for n pairs of lobe rotors (in this case n=4). The bottom most lobe rotor pair 2313 are held in position relative to the pump housing which in this case includes a step 2314 to define the pumping chamber for the bottom pair of lobe rotors 2313. In the embodiment shown the bottom separator plate 2308 rests atop of the step 2314. In another embodiment (not shown) a fourth separator plate with the end pieces is included to house the bottom-most pair of lobe rotors 2313 and their would be no step 2314. In this alternative embodiment there would be n separator plates for n pairs of lobe rotors.
To summarize an embodiment includes a lobe pump as in FIG. 23 (and FIG. 1, items 100, 101) comprising a housing 2301 (and FIG. 222201) forming a pump chamber, said housing having ends (e.g. 2202), an inlet and an outlet (seen in FIG. 21) and walls 2103, the walls having a height, an inner surface and an outer surface, and, end covers 2002 and 2202 that removable attach to each end of the housing and thereby seal the pump chamber, a first shaft 2003 and a second shaft, the shafts 2108 being elongated cylinders, the first shaft 2103 extending beyond a wall of the housing such that it is rotated by a motor, the shafts fixed within the housing such that their long axes are parallel, the shafts coupled through use of timing gears 302 affixed to a first end of each shaft such that rotation of the first shaft by the motor causes the second shaft to rotate, a plurality of segments 2004, each segment comprising a first lobe rotor 2104 having a center, a top surface, a bottom surface, sidewalls and a plurality of lobes symmetrically extending from the center, the lobes extended at a lobe separation angle from one another, the first lobe rotor fixedly attached to the first shaft through the center of the rotor such that rotation of the first shaft causes the first lobe rotor to rotate, a second lobe rotor, also seen as 2104, having a center, a top surface, a bottom surface, sidewalls and a plurality of lobes symmetrically extending from the center, the lobes extended at a lobe separation angle from one another, wherein the first lobe rotor and the second lobe rotor have the same number of lobes and lobe angles, the second lobe rotor fixedly attached to the second shaft through the center of the second lobe rotor such that the rotation of the second shaft causes the second lobe rotor to rotate, separation plates 2005 positioned above and below the first lobe rotor and the second lobe rotor adjacent to the top and bottom surfaces of the first lobe rotor and the second lobe rotor, said separation plates acting to physically isolate the segments from one another, and, each separation plate comprising, a flat plate having two ends, a top surface, a bottom surface and an edge. There are holes within the plate sized and position to allow passage of the shafts. End pieces are attached to each end of the flat plate, the end pieces being curved plates having a vertical height, an inner curved surface, an outer curved surface and a top edge and said end pieces projecting vertically at 90 degrees from the top surface of the flat plate. The radius of curvature of the inner curved surface selected for a tight fit to the sidewalls of the lobe rotors as they rotate (see FIG. 21) and, a radius of curvature for the outer curved surface selected to match a radius of curvature of the inner surface of the housing wall (also in FIG. 21). The vertical height of the end pieces is selected to provide a clearance for rotation of the lobe rotors. The end pieces are stacked upon one another such that the top surface of the end piece of the separator plate of one segment is contacted with the bottom surface of the flat plate in an adjoining segment (see FIG. 23). The shafts and the first lobe rotor and the second lobe rotor are positioned such that the simultaneous rotation of the first lobe rotor and the second lobe rotor results in meshing of the first lobe rotor and the second lobe rotor (see FIG. 21) thereby causes a pumping action wherein a fluid enters a central portion of each of the first lobe rotor and the second lobe rotor at the inlet of the housing, passes through a pump chamber isolation region, and the fluid is displaced from each of the first lobe rotor and the second lobe rotor at the outlet by the second lobe rotor and the first lobe rotor respectively. There is a separate pump chamber isolation region (near arrow 2109 in FIG. 21 and described in detail in FIG. 15) for each of the first lobe rotor and the second lobe rotor defined as a volume of space within the housing and delineated by the inner wall of the end piece and the lobe rotor, the pump chamber isolation region having a pump chamber isolation region arc 2109. In the plurality of segments, the first lobe rotors attached to the same shaft and in adjacent segments are aligned to be rotationally displaced from one another by an index angle (see FIG. 8), and the second lobe rotors attached to the same shaft and in adjacent segments are aligned to be rotationally displaced from one another by the index angle, the index angle is greater than zero.
In another embodiment there is a rotor assembly for a lobe pump. The rotor assembly is as described in FIG. 7 except that the separation plates are replaced with the separation plate shown in FIG. 19A or 19B.
SUMMARY
Designs for multiple segment lobe pumps are shown. The designs include pumps using rotors having two lobes to a plurality of lobes and segments that include two segments to a plurality of segments. Designs for both vertical, or straight walled conventional lobed rotors, as well as helical lobe rotors are shown. The designs are applicable to a variety of rotors and number of segments. In one particular case the designs enable a three lobe helical pump. Designs are also shown for separator plates used between the multiple segments. The separator float between the pairs of lobes in a segment and can also have a fixed position between the lobes by inclusion of end pieces that enable clamping of the separator plates in position.
Those skilled in the art will appreciate that various adaptations and modifications of the preferred embodiments can be configured without departing from the scope and spirit of the invention. Therefore, it is to be understood that the invention may be practiced other than as specifically described herein, within the scope of the appended claims.
Patent Application
20160281709
