• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Multipurpose fluid machine that has a rotor (2) coupled radially and axially to the interior of a housing (1), where the geometry of the rotor (2) in tune with that of the housing (1) can be designed with a multitude of configured shapes by pairs of arcs, not conditioned by regular, cylindrical shapes or symmetries. There are as many pairs of input-output paths (3 ', 3' '- 4', 4 '') as pairs of arcs conform to the rotor (2). The rotor (2) obeys a translational movement assisted by guiding means (5) housed in any part thereof (2). By simply interacting with the power supply of the input (3 ', 3' ') or output (4', 4 '') channels, it can operate without distinction as a generating, motor, reversing or transmitting machine, even as a motor and generator machine. Unison lacking axes that come out of the housing (1). (Machine-translation by Google Translate, not legally binding)
    公开号:ES2582011A1
    申请号:ES201630604
    申请日:2016-05-11
    公开日:2016-09-08
    发明作者:Manuel ÁLVAREZ LÓPEZ；Víctor CASTAÑO MARTOS；Gonzalo RUIZ MORALES
    申请人:Manuel ÁLVAREZ LÓPEZ；
    IPC主号:
    专利说明:

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    permanently radially and axially to the housing (1). The input (6) and output circuits
    (7) follow a uniformly increasing and decreasing cycle respectively, which can be reversed by simply changing the direction of translation of the rotor (2). On two occasions or intervals of a rotor cycle (2) sealed sealed chambers (8 and 9) are created that
    5 feed from the input circuit (6) and evacuate into the output circuit (7). The fluid displacement capacity of the system is equal to the sum of the volume of these two closed chambers (8 and 9).
    As stated before and later on, it will be seen, the rotor translation system (2) will be
    10 guarantees by at least one guiding means (5) that forces this type of movement, based on the eccentric rotation that would be produced by rotating a support or axis located in the rotor (2) around a support or axis located in the housing (1). The number of these guiding means
    (5) can be one to several and be housed anywhere in the rotor (2). In order to facilitate the understanding of these means for guiding (5) the translation, in the diagram (Fig-8a) a rotor (2) is shown with axle-like supports (11) rotating around axes (10) located in the housing (1). In diagram (Fig-8b) four intervals of translation of the rotor (2) on the housing (1) are described as a result of rotating the axes (10) in synchronization. It shows in diagrams (Fig-8c) a radial section, (Fig-8d) axial section and (Fig-8e) perspective of what being a single element is composed of two axes (10 and 11)
    20 displaced from each other to provide eccentric displacement.
    The translation guide means (5) comprise any system that already exists in the state of the art that provides rotation of a support around an axis (crankshaft effect), the detail set forth in (Figure-8) being only one shallow but practical sample for
    25 help understand the type of displacement.
    The possibility that the guiding means (5) that assist the translation can provide an adaptively variable eccentricity, would result in the reduction thereof, the loss of adjustment or sealing of the rotor (2) with the housing (1), up to extreme point where still turning the drive shaft (10) would not cause displacement to the rotor (2). In (Figure-9) we represent three example schemes where (Fig-9a) shows a full eccentricity that we have to point as preferred, where the rotor (2) has optimal radial adjustment to the housing (1). In (Fig-9b) we show how a medium eccentricity would act, maintaining the rotor (2) its axial adjustment or sealing with the housing (1) but distancing itself from its radial adjustment, not thereby canceling the displacement of the fluid, but reducing flow and pressure in the circuit. Operation in this state would resemble performance and


    benefits to rotodynamic type fluid machines losing the volumetric condition, but would outweigh the rest in that as eccentricity is controlled and adapted, the potential assistance to the circuit would alter its values with gains and advantages superior to those of any type of machine of rotodynamic fluid. In (Fig-9c)
    5 the axes (11) supported on the rotor (2) coincide with the center of the drive shaft (10), so even turning this last drive shaft (10) would not transfer any movement to the rotor (2), leaving the circuit open without any element that interrupts it.
    This fact explained above and represented with (Figure-9) shows that
    10 with a uniform motor we can go from a free circuit without any interruption (Fig-9c) to progressively reduce or increase flow on a whim by just applying an eccentricity calculated for this purpose (Fig-9b), or total and absolute interruption of the circuit getting an exact flow (Fig-9a). This means that the system perfectly meets the combined characteristics of the volumetric fluid machine and
    15 rotodynamics.
    Although there is a mandatory straight and flat axial contact or seal between the rotor (2) and the housing (1), this is due to a minimum extension equal to or greater than the diameter of the drive shaft (10). The same does not happen with contacts or radial sealing, which can be adapted to 20 geometries that do not comply with that obligation. In (Figure-10) three examples are shown in axial section of the system to understand that the geometry of the contact or radial seal between the housing (1) and the rotor (2) can be applied with a multitude of silhouettes. A rotor (2) with faces and straight edges is shown in the diagram (Fig-10a), in the scheme (Fig-10b) rotor (2) with straight faces and blunt edges, and in diagram (Fig-10c) a rotor (2) with faces and songs
    25 arches, this being variables that can be applied at the time of its design and manufacture to adjust the resulting model to the designer's own demands.
    All the development and schematization done so far have referred to a single arc-shaped rotor (2) that can be constructed with a multitude of shapes and geometries, without
    30 that means that it is the total of the invention, but the simplest variant that makes it possible to state more clearly the details and principles on which the system itself is based.
    Therefore, highlighting and considering that the rotor (2) in the form of an arc (With the possibility of
    35 different geometries) through its path or translation through the housing (1) makes contact or sealing with it by its outer and inner faces, and in turn in two moments
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    (14 ’and 14’ ’), as well as two axes (16) and (17) that are part of the means (5) that guide the translation. The scheme (Fig-13b) refers to the housing (1), where we find two pairs of input-output tracks (3'-4 'and 3' '- 4' ') located on the axial face (12) of the housing (1). In that same plane are the supports or internals (15) of the shafts (16) which, belonging to 5, the guiding means (5) of the translation can provide motility to the rotor (2). It is insisted that it is not conditioned on the number of these guiding means (5), but that it is at the discretion of the designer and the only limitation that his own design allows. In diagrams (Fig-13c) and (Fig-13d), by way of example it is cleared with two axial sections which could be a guiding means (5), where in (Fig-13c) the axis (16) is through to the outside of the housing (1) through the support or through (15) to provide or steal rotor motor (2), and in (Fig-13d) the shaft (16) is only housed or supported in the housing ( 1) in the support or intern
    (15) to guarantee the function of the guiding means (5). As mentioned previously, the guiding means (5) comprise any system already existing in the state of the art that provides rotation of a support around an axis (crankshaft effect),
    15 being the detail set out in (Figure-13) only a practical sample to help understand the type of displacement.
    In (Figure-14) we represent a complete cycle (per eighth of translation) to understand that the principle on which any system with multiple rotor of several arcs is based is the same as the one we had developed as a simple rotor of single arch
    We start in the scheme (Fig-14a) with a closed chamber (8) isolated from the entrance (3 ') and exit (4') tracks, plus an input circuit (6 '') with direct connection to the network 25 general suction (Admission) through the entry way (3 '') and an exit circuit (7 '') with direct connection to the general evacuation network through the exit way (4 '').
    Adding an eighth of translation to the rotor (2) we position ourselves in the scheme (Fig-14b), where on the one hand the previous closed chamber (8) becomes an output circuit (7 ') by 30 already having connection to the network generally through the exit route (4 '), and on the other the admission circuit (6') is started. Comparing with the previous interval, we see that the input circuits (6 ') and (6' ') have increased in volume and therefore there has been suction of the general network through the input routes (3') and ( 3 ''), as volume has been reduced in the output circuits (7 ') and (7' ') and therefore evacuation to the general network through the tracks
    35 output (4 ’) and (4’).
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    where an axle (16) supported on the housing (1) by means of first bearings (20) joins the two eccentric shafts (17) that rest on the rotors (2 'and 2' ') in a single element by means of second bearings (twenty-one). We reiterate that the means of translation guide (5) comprise any system already existing in the state of the art that
    5 provide rotation of a support around an axis (crankshaft effect), the detail shown in the scheme (Fig-16c) being only a shallow but practical sample to help understand the type of displacement.
    The proposed invention relates to a rotor (2) that moves adjusted inside the
    10 a housing (1), therefore the tool represented in the diagram (Fig-16b) should not be confused as a variant or alternative, since it is a set of rotors (2 'and 2' ') in series where each one moves adjusted to an internal cavity independent of housing (1). Similarly, series or parallel rotor assembly tools can be configured, but they always meet compositions that derive from the sum of the
    15 principle of the proposed invention.
    As many circuits result as pairs of input-output paths and these as many as pairs of faces or internal-external arcs in a single rotor (2), several flows of the same tool can be obtained if we interact with the input path feeding (3) and / or
    20 output (4).
    Based on (Figure-17), this would allow the option of each entry route (3 ’or 3’) that can be fed from the intake manifold (18) or the ejector manifold (19). When an input path (3 'or 3' ') is fed from the intake manifold (18) it results in 25 in that circuit (6'-7' or 6 '' - 7 '') a displacement of fluid from the intake manifold (18) to the ejection manifold (19), however, if we feed it from the ejector manifold (19) such displacement does not occur, since it would be feeding from the same place where it evacuates (remaining that circuit as null). In this way, as in a two-arc rotor we have two circuits (6'-7 'and 6' '- 7' ') we can obtain a full flow rate (Fig-17a) with the two input paths (3) feeding of the intake manifold (18),
    or half flow (Fig-17b and Fig-17c) if one of these routes is fed from the ejection manifold (19), since one of the circuits would have been void without providing fluid displacement from the intake (18) to the expulsion (19). This same applied to rotors of four arcs would result in a configurable tool with four different flows, that is,
    35 feed through a single entry route, two, three, or four. This configuration option can be applied through fixed or practicable shutter means in the


    manifolds, or means with bypass valves operated manually or remotely.
    The previous development has been based on conditioning the feeding of the entry routes (3 ’or 3’), but it would be the same if we do it with the evacuation of the exit routes (4 ’or
    5 4 ’’), that is, to condition the evacuation to the ejection manifold causing circulation of the fluid or to the intake manifold causing a recirculation that cancels the effectiveness of that circuit. That is, that you can interact interchangeably with the entry (3 ’or 3’ ’) or exit (4’ or 4 ’) routes to achieve the configuration described in the previous development.
    10 Referring to previous statements that the rotor arches (2) are not required to comply with symmetries and that different silhouettes can be applied independently, tools can be designed where the resulting closed chambers are all of different volume. In (Figure-18a) an example is shown with a rotor (2) of two arcs where all of them are different, thus resulting in a different volume of all
    15 closed cameras that conform (8 ’, 9’, 8 ’’ and 9 ’). A diagram showing the four closed chambers that would exist in a rotor translation cycle (2) is shown in (Figure-18b), and in the graph (Fig-18c) a bar is shown with the letter (A) which would mean 100% of the volume of the internal cavity of the housing. With the letter (B) a bar is divided in two to show that the rotor (2) occupies 43% of the internal cavity of the
    20 housing (1), 57% being free (23) for fluid displacement. It would be easy to deduce that this 57% corresponds to the fluid displacement capacity of the system, so it is possible to clear this deduction to prove that it is not true. That 57% is measured in any position of the rotor (2) inside the housing (1), but in a state of rest or static system. When the system is active fulfilling complete translation cycles, it
    25 make up several closed chambers and the system's displacement capacity is the sum of the volume of all of them. In the graph (Fig-18c) and bar identified with the letter (C) we show the proportion that would correspond to each of the closed chambers that would be created specifically in this example of (Figure-18). The camera (8 ’) would have a volume of 32% with respect to 100% of the internal cavity of the housing, the camera (9’) a
    30 7%, (8 ’’) 17% and (9 ’’) 16%, totaling 72%. That 72% is the true fluid displacement capacity of the system or tool with respect to its internal housing cavity (1), that is, that the system in dynamic state has a displacement capacity of 15% greater than when calculated in static (Depending on the rotor design that 15% may increase or decrease). In (Fig-18b) and (Fig-18c) it is identified as
    35 (22) the portion of the cavity of the housing where closed chambers are not formed, part of this dead space corresponding to the sum of the two pairs of entry tracks
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    to adopt the properties of rotodynamic pumps by simply reducing eccentricity in the means of guiding translation, or properties of volumetric pumps with the full eccentricity allowed by the design. It also stands out for being able to adopt irregular shapes, very useful to take full advantage of dead holes in its location. 5 It stands out because in addition to having the possibility of working as a generating machine
    or motor can do it like both at the same time, that is, pump driven by fluid motor in a single tool of a single rotor. Another outstanding feature is that different flow rates can be obtained by interacting on the feeding of the entry and / or evacuation routes of the exit routes, very useful for designing configurable standard pumps that can be
    10 can adapt to any situation at the same time of installation, as well as in the case of hydraulic or pneumatic engines the ability to design configurable transmissions and torque converters.
    The fluid machine set forth as the present invention complies with the four groups
    15 on which, depending on the direction of energy transfer, fluid machines can be classified in general, that is, which has the capacity to operate independently as a generating machine, motor machine, reversible machine or transmitter machine. According to its operating principle, it is embedded inside the volumetric fluid machines, but the system allows the option to control and adapt the eccentricity that
    20 guides the rotor translation by adopting the properties of rotodynamic machines.
    All this demonstrates the high innovative capacity that designers and designers would bring to the application of the present invention, taking advantage of much more functional, reduced and economical systems than the current ones.
    25 Sufficiently describing the nature of the present invention, as well as the manner of putting it into practice, it is stated that, within its essentiality, it may be implemented in other embodiments that differ in detail from that indicated by way of example, and to which it will also achieve the protection sought, provided that
    30 alter, change or modify its fundamental principle.
    权利要求:
    Claims (1)
    [1]
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    同族专利:
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    WO2017194801A1|2017-11-16|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US3999904A|1974-09-09|1976-12-28|Redskin Engines|Orbital piston engine|
    US4492539A|1981-04-02|1985-01-08|Specht Victor J|Variable displacement gerotor pump|
    US4606711A|1983-01-10|1986-08-19|Nippon Soken, Inc.|Fluid pump with eccentrically driven C-shaped pumping member|
    US5066207A|1990-05-08|1991-11-19|Valavaara William K|Rotary device|
    DE4218847A1|1992-06-09|1993-12-16|Manfred Max Rapp|Piston machine|
    DE19500774A1|1995-01-13|1996-07-18|Adolf Dr Ing Hupe|Rotary piston engine|
    DE102008025186B4|2008-05-23|2010-04-29|Manfred Max Rapp|Rotary engine|
    JP6125216B2|2012-12-14|2017-05-10|サンデンホールディングス株式会社|Scroll type fluid machinery|
    法律状态:
    2017-07-07| FG2A| Definitive protection|Ref document number: 2582011 Country of ref document: ES Kind code of ref document: B2 Effective date: 20170707 |
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    ES201630604A|ES2582011B2|2016-05-11|2016-05-11|POLIVALENT FLUID MACHINE.|ES201630604A| ES2582011B2|2016-05-11|2016-05-11|POLIVALENT FLUID MACHINE.|
    PCT/ES2017/070280| WO2017194801A1|2016-05-11|2017-05-05|Versatile fluid machine|
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