Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C3/00—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type
  • F04C3/02—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged at an angle of 90 degrees
  • F04C3/04—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C2/00—Rotary-piston machines or pumps
  • F04C2/02—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C2/00—Rotary-piston machines or pumps
  • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing

Definitions

• the present patent application relates to a new type of positive displacement rotary pump.
• the project presents different properties according to the established configuration.
• One of the configurations has a higher flow capacity than other types of positive displacement pumps.
• One of the models of the invention features an internal compression between the chamber elements, an ideal property for use in compressors.
• the perfect dynamic balance and robust geometry favor use at high speeds, favorable conditions for use as a high-power hydraulic motor.
• centrifugal pumps are the lowest cost alternative when pumping requires a high flow rate, with a low hold pressure sufficient.
• a commonly used option is multistage centrifugal pumps. These series pumps can have more than 40 stages. As the stages increase, the cost increases and the mechanical performance drops.
• turbo pumps and volumogenic pumps As turbo pumps have a reasonable mechanical performance and an excellent cost for use in low hold pressure in single-stage models, on the other hand, positive displacement pumps are capable of to reach high holding pressures with an excellent mechanical efficiency, however the flow capacity is low and the acquisition and maintenance cost is very high.
• the pumped volume is very high even when compared to some high flow centrifugal pumps of the same size driven by standard 2-pole electric motors, rotation close to 3600 rpm.
• a pump with internal turns of 120 mm in diameter and 50 mm in thickness (not counting the collectors, in the case illustrated, spikes) can pump more than 50 m 3 /hour at 3600 rpm. It is worth remembering that positive displacement pumps are capable of practically maintaining the flow as the hold pressure increases, unlike centrifugal pumps that present a sharp drop in flow in their flow x pressure curve.
• FIGURE 1 represents an exploded view of the “internal turns pumping system” in a high flow configuration with 8 inlets.
• FIGURE 2 represents the assembly in a radial section of the "internal turns pumping system" presented in figure 1,
• FIGURE 3 is a view of a 5-lobed protruding lobe gear used in the 8-inlet pump configuration.
• FIGURE 4 represents an inside view of a 4-input housing for use with 5-lobe lobed gears.
• FIGURES 5, 6 and 7 represent the trajectory of the toroidal thread that defines the generation of the spiral grooves of a pump with 8 inlets, the last figure being in section.
• FIGURE 8 represents a sectional view of an 8-inlet housing.
• FIGURES 9, 10, 11 and 12 represent assemblies of a pump configuration with internal compression in the configuration with a housing with 3 entrances containing the rotor 3 lobular gears with 12 lobes each.
• FIGURE 9 represents a view of the pump without the smooth casing.
• FIGURE 10 represents a view of the pump with only a casing of turns and the lobular gears in their respective positions.
• FIGURE 11 represents another higher view of figure 10 for the observation of internal compression.
• FIGURE 12 represents a sectional view of the pump assembly shown in Figure 11.
• FIGURES 13, 14 and 15 represent a pump with 4 inlets with 5 gears with 14 lobes with internal compression.
• FIGURE 13 represents a sectional view of the assembly for comparison with figure 12 with emphasis on the smallest distance between the grooves and turns.
• FIGURE 14 represents a view of the pump without the upper casing, the smooth casing.
• FIGURE 15 represents a view of the pump with only a 4-input coil housing and the 5 lobular gears in their respective positions.
• FIGURE 16 represents a side view of the 8-inlet pump showing the position of a cross-section orthogonal to a loop groove of the next figure.
• FIGURE 17 represents a view facing the region of the section shown in figure 16.
• FIGURE 18 represents a view of a side region of the 8-inlet pump with transparency in the turns housing.
• FIGURES 19, 20, 21 and 22 represent progressive sectional views of the 8-inlet pump assembly, the housing in figure 19 being uncut, showing its flat surface.
• FIGURE 23 represents a radial section of the assembly that was represented in figure 2, whose section is in a plane that passes outside the region of the lobular gears.
• FIGURE 24 represents a side view of a pump configuration with grooves and rectangular lobes without the upper casing.
• FIGURE 25 represents a side view of a pump configuration that presents 21 lobular gears in an inclined position, closer to the orthogonal planes to the trajectory defined by the spiral grooves. Only 3 consecutive lobular gears are present in the drawing.
• FIGURE 26 is a sectional view of an "internal loop pumping system” configuration with 16 inlets with a motor incorporated within the rotor.
• FIGURE 27 represents a view of the internal turns pumping system with 3 stages in a radial section.
• FIGURE 28 represents a view of the one-piece rotor.
• FIGURE 29 represents a sectional view of the one-piece rotor.
• FIGURE 30 is a photo of a prototype in the 8-inlet configuration geared towards high flow capacity.
• the “internal turns pumping system” is composed of 3 types of main elements.
• the “lobular gears” (4) present the pumping agents, the lobes (9), as well as a gear holds its teeth.
• a lobular gear is represented separately in figure 3.
• the “one-piece rotor” (25) is the central element that holds the lobular gears and has a “drive shaft” (5), the mechanism's drive shaft.
• the rotor also admits a split version on its equatorial plane to facilitate assembly or 3D printing. A few times in this text, to simplify the understanding of the rotor function, regardless of whether it is a split model or not, it will be treated as a rotor.
• the carcass is the external element, the wrapper, the cap that has spiral grooves on its inside.
• the project is composed of a pair of housings that are joined in their equatorial plane through the “central flange” (16) to enable assembly and closing.
• the use of models with both carcasses with the same format is foreseen without causing disadvantages, on the contrary, standardization is recommended and reduces costs.
• Some models feature a slightly or very different from the other housing depending on the purpose of the project configuration. A good example is that some configurations require one of the housings to be smooth internally, without any grooves.
• the carcass model without grooves is called “smooth carcass” (2).
• the "turn housings" (1) are the type housings that present the elements individually called “turn groove” (10).
• the set of grooves form a type of thread that describes a toroidal trajectory and admits to present more than one inlet
• figures 5, 6 and 7 illustrate the generatric trajectory of the grooves of the 8-inlet internal turns pumping system design.
• the “turn groove” is a type of thread or toroidal turn that presents a circular section in the cuts orthogonal to its trajectory, see figures 16 and 17.
• the two parts of the pair of housings are joined by screws installed in holes at the ends of the central flange (16).
• the housings can be joined in other ways, press fit, weld or glue.
• the “split rotor” consists of 2 parts arranged together in its equatorial plane. In said flat region, in the plane of union between the rotors, there is a half bearing support (11) to accommodate the "lobular gear axis" (12), the axis that passes to the center of the lobular gear.
• One of the pairs that make up the split rotor is the “shaft rotor” (6), which is characterized by having the “drive shaft” (5), a shaft long enough to reach the external region of the pump to be coupled to the available power source. .
• the pump works well even at low rotations, one being provided for manual operation or any other driving source, such as wind turbines, hydraulic turbines, electric motors, combustion engines, steam.
• the “solid rotor” (7) is the other part of the rotor of the split-type rotor model and admits to having a shorter shaft, the “secondary shaft” (26).
• One of the functions of the secondary shaft is to provide extra support when it is inserted into the housing of the turn housing.
• the so-called “secondary axis” is not a mandatory structure and can be suppressed from the project.
• the “one-piece rotor” is represented in figures 28 and 29, with figure 29 being cut to illustrate the bearings (11), hollow holes to allow the insertion and removal of the shafts of the lobular gears. For the purpose of illustration, only one axis is shown in figure 29.
• a toroidal-shaped curved inner surface defined by fitting with the shape of the side surface of the rotor that comes into contact with the inner surface must be machined. of the turns housing, that is, by the revolution of the rotor side profile design.
• This internal toroidal surface will be called “rotor sweep surface” (15). With groove machining turns the so-called “rotor sweep surface” becomes segmented. The region defined by the space between the edges of the grooves will be called “groove entrance”.
• Pumping chambers are defined by the action of the lobes to generate a movable closing area in the section of the pumping ducts.
• the “pumping ducts” are formed by the internal area of the “turn grooves” and by the toroidal surface of the rotors that touch the “rotor sweep surface” by waxing, sealing the “turn grooves” by closing the said region of the “groove entrance” ”.
• the rotation of the rotor causes a translation movement in the “lobular gears” under the action of the lateral force exerted on the “lobular gears” by the “radial slots” of the rotor.
• Said translation movement causes the rotation of the lobular gears because the gears are assembled with the “lobes” inserted, housed on the inner surface of the “turn grooves”, forcing the lobes to follow the path defined by the trajectory of the spiral grooves, generating the rotation of the grooves.
• lobular gears in sync with their translation.
• the lobular gears rotate freely (mounted only on the rotors) through their shaft which is supported by bearings present in the rotor.
• the lobular gears can work well, as they are also guided and centered by the engagement and constant contact of at least 2 of the 5 lobes of each lobular gear fitted in a spiral groove, with the lobular gear always supported. also by its lateral contact surface of its inner disk with said rotor sweeping surface.
• Said internal turns are composed of a type of thread that presents, in some configurations, a single and continuous complete trajectory, being described on the internal surface of the housing of turns.
• the complete trajectory of the design that generated the grooves of the 8-entry housing can be seen in figures 5, 6 and 7, with figure 7 being a central section, the complete designs in figures 5 and 6 are made up of only one continuous line, as in the drawing that defines the trajectory of the grooves, the groove at the beginning of a “turn groove” must coincide with the end of this same turn or another turn, a possibility in case there is more than one entry.
• Each of the housings admits to having a bearing (3), but there is the freedom to be defined in the project to support only one of the rotor shafts on a bearing in only one of the housings or to dispense with the adoption of bearings in both housings, especially if the pump is driven directly by a motor shaft, preferably a flanged type motor to ensure perfect alignment with the rotor shaft, eliminating the need for couplings and/or flexible joints between the motor shaft and the rotor. It is recommended a surface treatment and/or the adoption of a surface coating on the surfaces that will act on the bearing to reduce the friction between the parts.
• the adoption of synthetic material sleeves or bearings to act as a bearing between the shaft and the housing is foreseen and indicated.
• the coil housing can be the fastening element, the static part that can be fixed using feet or a flange fixed to the “central flange”. None prevents the spiral casings from rotating, whether the rotor shaft is static or rotating in the opposite direction.
• the radial symmetry of the project is favorable to the external movement of the referred carcasses.
• the “internal spiral pumping system” has several models, configurations in the most varied proportions, being more or less flattened, approaching more to the shape of a sphere or a disk according to the adopted configuration.
• the pump admits a configuration with an internal thread of only one inlet, as well as configurations with 10 inlets or more.
• the lobular gears have different numbers of lobes, and it is possible to define a lobular gear with more than 10 lobes, defined according to the design hold pressure at which the system will be applied, because the greater the number of lobes present in each groove, the greater the pressure reached by the system.
• Configurations that have more than 5 lobes are usually aimed at pumping gases and have a complementary housing without grooves and turns, the so-called “smooth housing” (2).
• the so-called “smooth housing” (2) To demonstrate the versatility of the number of inputs and lobes in lobular gears, 2 models will be presented. An example will be a configuration (figs. 9, 10, 11 and 12) of the pump with 3 inlets with 3 lobular gears with 12 lobes. Another configuration (figs. 13, 14 and 15) presented will be a pump with 4 inlets with 5 lobular gears with 14 lobes.
• each groove or inlet has 9 active lobes forming 7 chambers of decreasing volume towards the central discharge for each of the inlets, totaling 28 chambers, similar to what occurs in a pump scroll type. Due to the progressive reduction in the size of the chambers, these configurations are not suitable for pumping incompressible fluids.
• Configurations such as those exemplified with the smooth housing admit to have 2 or more lobular gears, whose maximum number of lobular gears is defined according to the project holding pressure in which the system will be applied, therefore, a greater number of lobular gears , allows more than one lobe to act on each expired groove at the same time in the spiral grooves in order to achieve a greater capacity for holding pressure.
• the number of lobes acting in each spiral groove would increase, providing a better seal and, consequently, a greater capacity to reach higher pressures.
• the distance to be defined between the grooves and turns can be changed, a greater distance between the grooves provides a better seal between the contact surfaces of the rotor and the turns housing, because the adjustment area or minimum contact between the “rotor sweeping surface” (15) and the toroidal side of the rotor becomes larger.
• the 3-inlet pump with 12-lobe gears has the lobes farther apart than the 14-lobe model, so the “rotor sweep surface” region is less prone to leakage.
• the configuration of the internal-turn pump with lobular gears of only 5 lobes and of the protruding type has the enveloping-type spiral grooves (10) to accommodate the most protruding lobes.
• the objective is to increase the area of the scanning section of the lobes so that the pumping ducts, that is, the internal region of the spiral grooves that define the pumping chambers, present a greater volume.
• the enveloping groove exceeds the diameter of the lobe, making the lobes embedded in the grooves spirals in the assembly.
• the 8-inlet pump Comparing “the internal loop pumping system” with 8-inlet encircling grooves with the 4-inlet configuration, the 8-inlet pump has a much higher volumetric capacity than the 4-inlet internal-turn pump. Both 115mm in diameter, the 8-inlet configuration of figure 30 pumps 260ml versus 150ml for around the 4-inlet configuration.
• the 4-inlet pump must have at least 2 opposing 5-lobe lobular gears, while the 8-inlet pump of the same external diameter must have at least 4 5-lobe lobe gears also equidistant to ensure that inside each pumping duct there is at least one lobe is present.
• the pump with 4 inlets has a smaller angle in the turns and therefore needs a lobular gear with a much smaller thickness.
• the 8-inlet pump Comparing the 4-inlet configuration with the 8-inlet configuration again, the 8-inlet pump, as it has a greater angulation in the turns, when turning only 90 degrees, the lobes completely cover the length of the grooves, therefore, it pumps the entire volume of the 8 pumping ducts 4 times each turn of the impeller drive shaft, this is one of the main factors for the high flow capacity.
• the 4-inlet pump in turn, requires half a turn for each lobe to travel the entire length of the spiral groove, greatly reducing the flow capacity.
• the lobular gears in the 4-input pump rotate 4/5th of a turn while in the 8-input pump the lobular gears rotate 8/5th of a turn for each rotation of the drive shaft.
• the 4-inlet pump Due to the lower rotation of the lobular gears, the 4-inlet pump has a smoother movement and less wear as it has fewer lobes passing through the spiral groove at each rotation. On the other hand, due to its smoother operation due to the smaller angle of the turns and the lower rotation of the lobular gears, the 4-inlet pump is better able to rotate at a higher maximum rotation, a condition of greater wear that would partially compensate for the lower volumetric capacity. Similarly, the 8-inlet model, when rotating at a speed 40% lower than the 4-inlet model, still has a slightly higher flow rate.
• the “pumping system of internal turns” is suitable to be mounted in series in order to achieve a higher holding pressure in relation to the use of only one stage.
• the multistage configuration can be seen in a radial sectional view of a 3-stage assembly, figure 27.
• the said "coupling sleeve" logically presents 3 keyways where the keys are inserted .
• the keys are hidden in the drawing as they are inside the coupling sleeves.
• the project admits the adoption of a splined shaft compatible with the internal spline to be adopted in the coupling sleeve.
• the coupling sleeve is therefore inserted into the joint region between the shafts of each stage.
• the “coupling collector” (22), a sleeve with a type of coupling at both ends, in the case shown the coupling collector is a cylinder with a continuous external thread. Therefore, the “coupling manifold” performs the function of joining the stages so that the discharge of the previous stage is coupled to the suction of the next stage.
• the “internal turns pumping system” admits to having 10 stages or more, as mentioned, it will depend on the pumping pressure to be required by the project.
• Figure 16 shows the position of the orthogonal section in relation to a loop groove and figure 17 a cross-sectional view of the outermost lobe.
• Figure 18 shows the housings of internal turns with transparency. Through this transparency it is possible to observe a zigzag spot (18) formed by the contact line between the lobular gear and the spiral grooves.
• the thickness of the inner part of the rotor that is, the region between the axis and the beginning of the toroid surface, must be defined so that the length of the path of the path of the lobes in this inner region of the rotor, allows that during the return of the lobes to the interior of the rotors, at least one of the lobes is present in this path described inside the rotors, this passage channel of the lobes is called “reflow channel” (17).
• the objective is to always keep this section obstructed by at least 1 lobe to avoid a free return of fluid in this region.
• 2 lobes are located inside the radial slot of the rotors, one at the inlet and the other in the region close to the outlet of the “reflow channel”, preventing the free flow return in this region of the radial slot of the rotors. rotors.
• the lobular gear In the operating position shown in figure 12, only one lobe is present in the reflux channel and in figure 13 the lobular gear is in the position that presents 2 lobes in the reflux channel, always guaranteeing the obstruction of the "reflow channel”.
• Figures 19, 20, 21 and 22 are consecutive cuts in the design of the 8-inlet pump to demonstrate, from another angle, the perfect fit between the lobes and the spiral grooves.
• Figure 23 is a representation of the 8-inlet pump in a radial section outside the lobular gears region to demonstrate the fit between the toroidal side surface of the rotors and the rotor sweep area (15).
• the pumping pressure acts by exerting a lateral force on the lobular gears through the contact line between the lobe and the inner surface of the spiral grooves, this contact line of the lobe can be observed in detail 18 of figure 18
• This reaction force to the pumping interferes little against the rotational movement of the lobular gears, since the angle between the reaction force to the pumping exerted on the lobes is close to the perpendicular to the face of the lobe. Therefore, the closer the angle between the face of the lobe and the path of the groove turns to the perpendicular, the better it will be for the greater durability of the pump.
• the smaller the pitch angle of the toroidal thread the closer the angle between the direction of the force applied by the fluid pressure and the side surface of the lobes will be to the perpendicular.
• Surface treatment or coating with metals suitable for acting as bearings on the surface of the lateral region of the central disk of the lobular gear and on the lateral surface of the radial slots is foreseen.
• the reflux in this region occurs in the direction of the region of higher pressure to a region of lower pressure, it interconnects the settlement with the suction, transferring torque to the lobular gears and in this process, depending on the configuration, it is possible to make the lobular gears conductive in their rotational movement. instead of being driven by the spiral grooves.
• the condition of the lobular gears having a driving source in addition to the rotation defined by the spiral grooves leads to lower surface pressures between the lobes and the spiral grooves, therefore, less wear and vibrations.
• the “lobes” admit of having a rectangular shape (figure 24), continuing to bulge on their sides, with the piece in this rectangular shape being called “rectangular gear” (19).
• the shape of the spiral grooves would be changed to adapt to this new shape of the lobes, being called “rectangular spiral groove” (20).
• This new geometry of the lobes and grooves of the turns aims to increase even more the volumetric capacity of the “internal turns pumping system”. This type of pump with rectangular lobes will be called “Pump with rectangular internal turns”.
• the pump with internal turns has a version in which the lobular gears are arranged obliquely, seeking to be closer to the orthogonal position in relation to the grooves, as can be seen in the geometric study presented in Figure 25.
• One of the objectives of the lobular gears is to be in a plane that is as orthogonal as possible to the section of the pumping ducts already discussed above, is related to a reduction in wear due to the decomposition of the reaction forces to the pumping that act on the lobes, preventing the pressure exerted on the fluid during pumping to generate opposing forces. to the rotational drive of the lobular gear.
• This geometry allows for a greater number of lobular gears as they can be much narrower, the pump may have more inlets and a greater volumetric capacity, much larger than the 8-inlet pump cited as an example. Another factor would be a lower volume of reverse pumping due to the smaller thickness of the lobular gears, resulting in a narrower “reflow channel” and, therefore, a smaller volume between the lobular gears in the “reflow channel”.
• This configuration of the internal-turn pump with the lobular gears on an inclined plane would be called an “oblique-gear internal-turn pump”.
• the design of the concept pump in figure 25 presents 21 inlets and 21 lobular gears presenting 3 lobes acting in each groove.
• FIG 26 it is possible to observe the variations in the design configuration that allow the rotor to have a larger internal space to the point of fitting a motor (21).
• an electric motor is represented inside the pump rotor, its housing being fixed to said rotor, the axis of said motor being fixed in one of the housings of internal turns.
• Parts of pumps with internal turns can be manufactured via injection in plastic or resins, printed (with thermoplastics or metals), sintered (powder metallurgy), cast in lost wax by the microfusion process and/or machined.
• Surface treatment on parts is an option as a device to increase durability in low-cost machining metals such as aluminum, another option is chemical coatings with low friction coefficient and self-lubricating.
• the “internal loop pumping system” acts as a motor, when coupled to a pressurized fluid in one of its collectors, being suitable for use in hydroelectric plants due to its reduced size compared to other positive displacement pumps.
• the “internal loop pumping system” can act as a motor using pressurized gas streams as energy sources when a source of steam pressure, pressurized air or pressurized gases from the burning of fuels is coupled to one of its collectors. When designed to perform the function of a motor, it is called an “internal-turn motor”.
• the “internal turns pumping system” is expected to perform the function of a hydraulic pump and, when designed for this function, it is called an “internal turns pump”.
• the “pump with internal turns” admits several uses. It is intended to be used as a water pump for pumping clean or dirty water, with abrasive particles such as sand or less abrasives, food pump, sanitary pump, oil pump, fuel pump, hydraulic fluid pump, hemodialysis pump, auxiliary heart pump for internal or external use or in artificial heart function. It has a good suction capacity due to its long stroke expansion in the pumping ducts, similar to piston systems.
• the pump with internal turns is indicated for use as a heart pump for internal use because it is very compact and has a small internal surface in relation to its flow capacity, a favorable factor to generate less rejection in contact with the blood, thus, it is also indicated for use as a hemodialysis pump.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Rotary Pumps (AREA)
• Details And Applications Of Rotary Liquid Pumps (AREA)

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Citations (8)

• 2021
  • 2021-03-07 BR BR102021004295-8A patent/BR102021004295A2/pt unknown
• 2022
  • 2022-03-02 CN CN202280020008.7A patent/CN117083458A/zh active Pending
  • 2022-03-02 WO PCT/BR2022/050067 patent/WO2022187920A1/pt active Application Filing
  • 2022-03-02 EP EP22765390.4A patent/EP4306801A1/de active Pending

Patent Citations (8)

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