• 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:
    A volumetric pump (1) comprises a casing comprising a central body (2) and two closing covers (20), in said central body (2) being formed two communicating cylindrical chambers (22, 23), a suction duct (I ) and a delivery duct (O), and two rotors (3, 4) rotatably mounted in said chambers (22, 23) of the central body and supported by respective shafts (5, 6) rotatably mounted in said closing covers (20 ). The two rotors (3, 4) comprise: a male rotor (3) which comprises only protuberances (30) and does not provide slots, and a female rotor (4) which includes only slots (40) and does not provide teeth or protuberances.
    公开号:CH708632B1
    申请号:CH01436/14
    申请日:2014-09-23
    公开日:2018-06-29
    发明作者:Tommasini Franco
    申请人:G P S Green Power Solution Sa；
    IPC主号:
    专利说明:

    Description [0001] The present patent application for industrial invention relates to a volumetric gear pump.
    [0002] Various types of internal gearing volumetric pumps are known on the market for transporting liquid or gaseous fluids from a suction duct to a pump delivery duct.
    [0003] In fig. 1 shows a volumetric gear pump, according to the prior art, indicated as a whole with the reference number (101). The pump (101) comprises a housing (102) provided with a suction duct (I) and a delivery duct (O). Two identical rotors (103) are mounted within the housing (102). Each rotor (103) comprises a gear consisting of a toothed wheel. That is, each rotor comprises a plurality of straight or helical teeth (130), which define a plurality of slots (131) between the teeth (130).
    [0004] The two gears (103) mesh with each other, so that the teeth (130) of one gear engage in the slots (131) of the other gear and vice versa. In this way, a fluid enters the intake duct (I) and exits from the delivery duct (O).
    [0005] This type of known volumetric pumps has some drawbacks due to the phenomenon of encapsulation of the fluid. In fact the fluid treated by the pump is trapped in the slots of a rotor and is compressed by the teeth of the other rotor, generating micro-explosions. These micro-explosions significantly limit the rotor speed, cause considerable rotor wear and generate break points in the rotor teeth.
    [0006] Vane pumps are also known which comprise a rotor provided with cavities within which the blades radially slide. The rotor is mounted eccentrically with respect to the housing of the casing which houses it and the blades are stressed by springs or by the centrifugal force towards the surface of the rotor seat.
    [0007] These vane pumps allow a limited number of revolutions, involve an early wear of the vanes and require lubrication with oil and therefore a separator which sprays the oil from the fluid treated by the pump.
    [0008] US 2011/0 135 525 describes a non-eccentric motor which includes male-type rotors provided with female-like projections and rotors provided with cavities in which the projections of the male rotors engage. However, in particular the male rotors have a particular conformation of the protrusions which are difficult to achieve since they are formed in a single piece with the rotor body.
    [0009] The object of the present invention is to obviate the drawbacks of the prior art by providing a volumetric gear pump which is able to avoid the encapsulation of the fluid.
    [0010] Another object of the present invention is to obtain such a volumetric gear pump that can operate at a high number of revolutions and at the same time is extremely reliable and safe.
    [0011] These aims are achieved according to the invention with the characteristics listed in the appended independent claim 1.
    [0012] Advantageous embodiments appear from the dependent claims.
    [0013] The volumetric pump according to the invention comprises: - a carcass comprising a central body and two closing covers, in said central body being formed two communicating cylindrical chambers, an intake duct and a delivery duct, and - two rotors mounted rotatable in said chambers of the central body and supported by respective mounted shafts rotatably supported in said closing covers.
    [0014] The two rotors comprise: - a male rotor which comprises only protuberances and does not provide slots, and - a female rotor which comprises only slots and does not provide teeth or protuberances.
    [0015] The male rotor meshes with the female rotor, i.e. the protuberances of the male rotor engage in the grooves of the female rotor, without contact between the two rotors when the two rotors are stationary. The provision of the male rotor and the female rotor, allows to avoid the encapsulation of the fluid in the female rotor slots. As a result, the pump according to the invention can be used at a high number of revolutions, with minimal stress on the moving mechanical parts.
    [0016] In particular, the male rotor comprises a cylindrical body provided with seats. The protuberances consist of sectors comprising a base which engages in the seat of the cylindrical body of the rotor. This characteristic allows easier realization of the protuberances in accordance with predetermined geometries, as will be described below. Moreover, the female rotor and the male rotor are arranged next to each other and the delivery and suction ducts are arranged on one side and on the other with respect to the rotors and have orthogonal axes between them.
    [0017] Further characteristics of the invention will appear more clearly from the detailed description which follows with reference to the attached drawings, which are only illustrative and not limiting, where: fig. 1 is a cross-sectional view of a volumetric gear pump according to the prior art; Fig. 2 is a perspective view, showing an exploded view of the volumetric gear pump according to the invention; Fig. 3 is a cross-sectional view of the pump in fig. 2 assembled; Fig. 4 is an exploded view of a male rotor of the pump in fig. 2; Fig. 5 is a perspective view, showing an exploded view of a variant of the pump in fig. 2; Fig. 6 is a perspective view illustrating an exploded view of a second embodiment of the pump according to the invention; Fig. 7 is a perspective view of the pump in fig. 6 assembled; Fig. 8 is a perspective view of the pump in fig. 7 sectioned axially; Fig. 9 and 10 are cross-sectional views of the pump of Fig. 7 sockets in two different rotor positions; and fig. 10A is an enlarged detail of fig. 10.
    [0018] For now with reference to figs. 2, 3 and 4 describes the volumetric pump according to the invention, indicated as a whole with the reference number (1).
    [0019] The pump (1) comprises a casing comprising a central body (2), sealed by means of two closure covers (20) in the form of plates.
    [0020] The central body (2) comprises two communicating cylindrical chambers (22; 23), so as to form a substantially "8" -shaped opening which is sealed by the two covers (20). In the central body there are two ducts (I, O) communicating with the outside, respectively for suction and delivery of the fluid treated by the pump.
    [0021] A male rotor (3) and a female rotor (4) are arranged in the cylindrical chambers (22, 23) of the central body. The male rotor (3) includes only protuberances (30) and does not include any slots. Instead the female rotor (4) comprises only slots (40) and does not provide teeth or protuberances. The male rotor (3) meshes with the female rotor, that is, the protuberances (30) of the male rotor engage in the slots (40) of the female rotor, without contact between the two rotors.
    [0022] The male and female rotors (3, 4) are mounted on respective shafts (5, 6). The rotor shafts (5, 6) are rotatably supported in supports (bushings or bearings, not shown in the figures) provided in seats (24) of the covers (20).
    [0023] Preferably the shaft (6) of the female rotor is intended to be connected to a drive shaft. Therefore, the female rotor (4) is the driving gear and the male rotor (3) is the driven gear. However, also the shaft (5) of the male rotor can be connected to a drive shaft or even both shafts (6, 5) of the rotors can be connected simultaneously to two drive shafts, so as to obtain a better distribution of the force couples work.
    [0024] According to the direction of rotation of the motor shaft, the ducts (I, O) of the central body can act as a suction duct or delivery duct.
    [0025] Advantageously, two external gears (7, 8) are arranged outside the casing and keyed to the rotor shafts (5, 6). The external gears (7, 8) are toothed wheels that mesh with each other. The external gears allow the male and female rotors (3, 4) to be put in phase; that is, during the rotation of the two rotors the protuberances (30) of the male rotor enter the slots (40) of the female rotor.
    [0026] With reference to fig. 3, the male rotor (3) comprises a cylindrical body (35) and a plurality of protuberances (30) which project radially from the cylindrical body (35). Each protuberance (30) in cross section comprises two flank-shaped sides (31,32) that converge into a rounded or flat head (33). The flank-shaped flank is a curve that has an inflection. The inflection is a point on a curve in which the curvature or concavity changes sign from positive to negative or from negative to positive. The curve changes from concave (positive curvature) to convex negative curvature or vice versa.
    [0027] The two sides (31,32) of a protuberance are symmetrical to each other, with respect to an axis of radial symmetry passing through the head (32) of the protuberance.
    [0028] Advantageously, the male rotor (3) comprises two protuberances (30) in diametrically opposite positions. In this case, in the chamber (22) of the central body of the carcass a suction area (A) is defined which communicates with the suction duct (I) and a delivery area (B) communicating with the delivery duct (O).
    [0029] The female rotor (4) comprises a cylindrical body (45) in which a plurality of cavities (40) are formed which extend radially. Each slot (40), in cross section, comprises an inlet side (41) and an exit side (42) in the form of an inflection which connect in a concave bottom surface (43). The profiles of the two sides (41, 42) of the quarry are not symmetrical with respect to a radial line passing through the bottom of the quarry. The flexed profile of the inlet side (41) is shorter and has a greater curvature than the flexed profile of the exit side (42) of the slot. The flexed profile of the exit side (42) is almost straight.
    [0030] Advantageously, the female rotor (4) comprises two slots (40) in diametrically opposite positions.
    [0031] The heads (33) of the protuberances of the male rotor are very close to the inner surface of the cylindrical chamber (22), and during operation, the heads (33) of the protuberances of the male rotor reach a short distance from the bottom (43) of the quarry, so as to avoid the passage of liquid. However, the heads (32) of the protuberances do not touch the inner surface of the cylindrical chamber (22) nor the bottom (43) of the grooves of the female rotor.
    [0032] Furthermore, the outer surface of the cylindrical body (45) of the female rotor is almost tangent to the inner surface of the cylindrical seat (23) of the central body of the casing, so as to avoid the passage of liquid.
    [0033] Similarly, the outer surface of the cylindrical body (45) of the female rotor is almost tangent to the outer surface of the cylindrical body (35) of the male rotor.
    [0034] The male rotor (3) and the female rotor (4) are perfectly centered in their respective cylindrical seats (22, 23) so as to leave a tolerance space of 0.05 mm, preferably 0.02 mm, between the following parts: - between the heads (33) of the protuberances of the male rotor and the inner surface of the cylindrical chamber (22) of the central body, - between the heads (33) of the protuberances of the male rotor and the bottom surface (43) of the female rotor slots, - between the outer surface of the cylindrical body (45) of the female rotor and the inner surface of the cylindrical seat (23) of the central body of the casing, - between the outer surface of the cylindrical body (45) of the female rotor and the outer surface of the cylindrical body (35) of the male rotor.
    [0035] In fig. 3 illustrates an embodiment, in which the male rotor (3) has a head diameter (intended as the distance between the heads (33) of two diametrically opposite protuberances) equal to the diameter of the cylindrical body (4) of the female rotor, so as to have two chambers (22, 23) of equal diameter and simplify the synchronization of the two rotors. However, when the diameter of the cylindrical body (35) of the male rotor (3) is smaller than the diameter of the cylindrical body (45) of the female rotor (4) it is mandatory to have a minimum tolerance between the two cylindrical bodies (35, 45) because the peripheral speeds of the two cylindrical bodies (35, 45) are not equal and touching one would have a considerable friction that would prevent the rotation of the two rotors.
    [0036] To solve this drawback, the diameter of the cylindrical body (35) of the male rotor can be equal to the diameter of the cylindrical body (45) of the female rotor. In this way, the peripheral speed of the two cylindrical bodies (35, 45) of the two rotors is the same and the tolerance between cylindrical bodies (35, 45) of the two rotors can be brought to zero, allowing a contact between the cylindrical bodies ( 35, 45) of the two rotors in the rotation phase. As a result, losses are minimized and high rotation speeds are allowed. Moreover, in this case, the chamber (22) which houses the male rotor (3) is larger than the chamber (23) which houses the female rotor (4) and in this way also increases the flow rate of the pump (1), maintaining the same size as the protuberance module (31).
    [0037] It must be considered that the particular shape of the slots (40) of the female rotor and the fact that there are no parts in contact between the rotors (3, 4) and the casing, allow the pump (1) not to trap fluid, to operate at high rpm and to limit wear and tear of mechanical parts.
    [0038] With reference to fig. 4, the male rotor (3) is made of several parts that can be assembled together. For example, in the cylindrical body (35) seats (36) are obtained having a substantially C-shaped or dovetail profile, in cross-section.
    [0039] In this case the protuberances (30) consist of sectors provided with a substantially parallelepiped-shaped base (34) which engages in the seat (36). In the base (34) of the protuberance there may be provided ribs or guide grooves (34 ') which engage with complementary guide ribs or grooves (36') provided in the seat (36) of the cylindrical body of the male rotor.
    [0040] The entire rotors (3, 4) or only the protuberances (30) and / or the slots (40) can be subjected to thermal and / or chemical treatments and can be coated with suitable materials, such as hard metal, widia, rubber, plastic, teflon or ceramic.
    [0041] With reference to fig. 5, the pump (1) also includes two sealing gaskets (9) consisting of "8" shaped plates made of anti-friction and self-lubricating material. The seals (9) are located between the central body (2) and the covers (20). For this purpose, special recessed seats (25) suitable for housing the sealing gaskets (9) are formed in the surface of the lids facing the central body. Springs (90) are arranged in the seats (25) of the covers so as to urge the sealing gaskets (9) towards the central body. In this way, the sealing gaskets (9) abut against the flat faces of the male and female rotors (3, 4). This solution allows to obtain a watertight seal of the chambers (22, 23) formed within the central body (20), avoiding any loss due to construction tolerances. In this way, even if the rotors (3, 4) are coated with an anti-friction and self-lubricating material, the pump (1) can be used at a high number of revolutions, without oil and with minimal wear on the moving mechanical parts.
    [0042] With reference to Figures 6-10, a pump (201) is described according to a second embodiment of the invention, in which elements equal to or corresponding to those already described, are indicated with the same reference numbers and the their detailed description.
    权利要求:
    Claims (11)
    [1]
    [0043] The pump (201) comprises a male rotor (3) having a body (35) with a double diameter with respect to the body (45) of the female rotor. In this case the female rotor (4) rotates at twice the speed of the male rotor; therefore the male rotor (3) has two diametrically opposite projections (30) and the female rotor (4) has only one slot (40). [0044] With reference to fig. 9, the female rotor (4) and the male rotor (3) are arranged one next to the other. The pump (201) comprises: - a suction duct (I) arranged above the chambers (22, 23) of the two rotors, and - a delivery duct (O) arranged under the chambers (22, 23) of the two rotors and having an axis perpendicular to the axis of the intake duct (I). [0045] This description relates to the arrangement of fig. 9, clearly the pump can be rotated as desired. The important thing is that the delivery and suction ducts (I, O) are arranged on one side and the other with respect to the rotors (3, 4) and have orthogonal axes between them. [0046] In this way the male rotor (3) rotates in the direction of the arrow (R1) and the female rotor (4) rotates in the direction of the arrow (R2). [0047] Advantageously the delivery duct diameter (O) is greater than twice the diameter of the suction duct (I), so as to facilitate the expulsion of the liquid, without creating counter-pressures in the chamber (23) of the female rotor (4) , under the female rotor (4), since these counter-pressures would be in contrast with the direction of rotation (R2) of the female rotor. In fact, possible back pressures would push in the groove (40) of the female rotor in contrast to the direction of rotation (R2) of the female rotor. [0048] With reference to fig. 10, during the meshing phase of the projection (30) of the male rotor in the groove (40) of the female rotor, an empty space (D) is generated (shown in broken lines), under the meshing portion of the rotors, towards the delivery duct ( OR). This empty space (D) is completely empty of liquids, so as not to create pressures that contrast the rotational directions (R1, R2) of the rotors (3, 4). [0049] The configuration of the chambers (22, 23), the dimensions of the rotors (3, 4) and the arrangement of the suction (I) and delivery (O) ducts allow an easy expulsion of foreign bodies (E) which can enter in the intake duct (I). These foreign bodies (E) never fit between the slots (40) of the female rotor and the projections (30) of the male rotor. [0050] A grid (29) is placed at the inlet of the intake duct (I). The size of the foreign bodies (E) is defined by the measurements of the holes in the grille (29) which must always be less than the measurement of the space (S) between the diameter of the male rotor body and the diameter of the seat (22) of the male rotor. That is, this space (S) is substantially equal to the length of the protuberances (30). Therefore the holes of the grid (29) have a diameter smaller than the length of the protuberances (30) of the male rotor. [0051] With reference to fig. 10A, the outlet side (42) of the groove (40) is defined between a point P1 connecting to the circumference of the body (45) of the female rotor and a point P2 connecting to the bottom (43) of the groove. The inlet side (31) of the projection (30) is defined between a connecting point F1 with the circumference of the body (35) of the male rotor and a point F2 connecting with the head (33) of the male rotor. The segment between P1 and P2 must be longer than the segment between F1 and F2. In other words, the rope (C) that underlies the exit side (42) of the groove must be greater than the rope (H) which subtends the entrance side (31) of the projection. [0052] In this way the liquid under pressure, trapped in the space between the inlet side (31) of the protrusion and the outlet side (42) of the groove, does not create forces opposing the normal direction of rotation of the two rotors. In this way we obtain a rotary movement of the two rotors (3, 4) without dead spots. [0053] With reference to figs 6, 7 and 8, the central body (2) is arranged between two sealing plates (209). On the outside of each sealing plate (209) is mounted a first impeller (G1) connected to the shaft (5) of the male rotor and a second impeller (G2) connected to the shaft (6) of the female rotor. In this case, respective chambers (26a, 26b) are formed in the inner surface of the covers (20) in which the impellers (G1, G2) can rotate, the chambers (26a, 26b) of the impellers communicate with exhaust ducts (27a, 27b). [0054] In this way, any leaks of fluids passing through the sealing plates (209) are centrifuged by the impellers (G1, G2) in the chambers (26a, 26b) of the impellers and conveyed into the exhaust ducts (27a, 27b) obtained in the covers (20). As a result, there are no working pressure limits dictated by para-oils or para-dust (300) mounted around the rotor shafts. This allows the use of common oil seals or dust seals (300) to isolate the fluids from any machines or generators applied on the main transmission shaft. [0055] Equivalent variations and modifications can be made to the present embodiments of the invention, within the reach of a person skilled in the art, which in any case fall within the scope of the invention. claims
    1. Volumetric pump (201) comprising: - a casing comprising a central body (2) and two closing covers (20), in said central body (2) being formed two communicating cylindrical chambers (22,23), a conduit of suction (I) and a delivery duct (O), and - two rotors (3, 4) rotatably mounted in said chambers (22, 23) of the central body and supported by respective shafts (5, 6) rotatably mounted in said covers closing (20), said two rotors (3, 4) comprise: - a male rotor (3) which includes at least one protuberance (30) and does not provide slots, and - a female rotor (4) which includes at least one groove ( 40) and does not comprise teeth or protuberances, in which the male rotor (3) meshes with the female rotor, ie the at least one protuberance (30) of the male rotor engages in the at least one groove (40) of the female rotor, without contact between the two rotors when the two rotors are stationary, and the male rotor comprises a cylindrical body (35) provided with at least one seat (36) and said at least one protuberance (30) consists of a sector comprising a base (34) which engages in said seat (36) of the cylindrical body of the rotor; in which the female rotor (4) and the male rotor (3) are arranged one next to the other and the delivery and suction ducts (I, O) are arranged on one side and the other with respect to the rotors (3, 4) and have orthogonal axes between them.
    [2]
    2. Pump (201) according to claim 1, wherein said male rotor (3) comprises a cylindrical body (35) and at least one protuberance (30) which protrudes radially from the cylindrical body and said female rotor (4) comprises a cylindrical body (45) and at least one groove (40) extending radially within the cylindrical body.
    [3]
    3. Pump (201) according to claim 2, wherein - each protuberance (30) of the male rotor, in cross-section, comprises two flank-shaped sides (31, 32) that converge into a flat or rounded head (33) the two sides (31, 32) of a protuberance being symmetrical to each other, with respect to an axis of radial symmetry passing through the head (33) of the protuberance, and - each slot (40), in cross section, comprises two sides (41 , 42) in the form of an inflection that are connected in a concave bottom surface (43), in which the profiles of the two sides (41, 42) of the groove are not symmetrical with respect to a radial straight line passing through the bottom of the groove , the flexed profile of the inlet side (41) having a greater curvature than the flexed profile of the exit side (42) of the slot.
    [4]
    4. Pump (201) according to claim 3, wherein the rope (C) that underlies the exit side (42) of the groove is greater than the rope (H) which subtends the entrance side (31) of the projection.
    [5]
    5. Pump (201) according to claim 3 or 4, wherein the male and female rotors (3,4) are centered in the chambers (22,23) of the central body so as to leave a tolerance space of 0.05 mm, preferably 0.02 mm, between the following parts: - between the heads (33) of the protuberances of the male rotor and the inner surface of the cylindrical chamber (22) of the central body, - between the heads (33) of the protuberances of the male rotor and the bottom surface (43) of the grooves of the female rotor, - between the outer surface of the cylindrical body (45) of the female rotor and the inner surface of the cylindrical seat (23) of the central body of the carcass, - between the outer surface of the body cylindrical (45) of the female rotor and the outer surface of the cylindrical body (35) of the male rotor.
    [6]
    6. Pump (201) according to one of the previous claims, wherein the male rotor (3) has two diametrically opposite protuberances (30) and the female rotor (4) has a slot (40).
    [7]
    7. Pump (201) according to one of claims 2 to 6, wherein the cylindrical body (35) of the male rotor has a diameter twice the diameter of the cylindrical body (45) of the female rotor.
    [8]
    8. Pump (201) according to one of the previous claims, further comprising two external gears (7,8) constituted by toothed wheels keyed on the shafts (5, 6) of the rotors on the outside of said carcass.
    [9]
    9. Pump (201) according to one of the previous claims, wherein said delivery duct (O) has a diameter greater than twice the diameter of the intake duct (I).
    [10]
    10. Pump (201) according to one of the preceding claims, further comprising a grid (29) placed at the inlet of the suction duct (I), said grid having holes with a diameter smaller than the length of said protuberances (30) of the male rotor.
    [11]
    11. Pump (201) according to one of the preceding claims, further comprising: - two sealing plates (209) arranged between the central body (2) said closing covers (20), - two first impellers (G1) connected to the shaft (5) of the male rotor on the outside of said sealing plates (209), - two second impellers (G2) connected to the shaft (6) of the female rotor on the outside of said sealing plates (209), and - respective chambers (26a, 26b) formed in the inner surface of the lids, in which the impellers (G1, G2) can turn, said chambers (26a, 26b) of the impellers communicating with exhaust ducts (27a, 27b) formed in said covers (20 ).
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    同族专利:
    公开号 | 公开日
    CH708632A2|2015-03-31|
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    RU2016115597A|2017-10-26|
    US20160230760A1|2016-08-11|
    EP3049622A1|2016-08-03|
    WO2015044969A8|2015-10-22|
    CA2924421A1|2015-04-02|
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    WO2015044969A1|2015-04-02|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US1052045A|1912-02-20|1913-02-04|Andrew G Doedyns|Rotary engine.|
    GB749569A|1954-04-15|1956-05-30|Karsten Alfred Ovretveit|Improvements in or relating to rotary fluid pumps and motors and the like|
    NL111999C|1955-04-01|
    US4526518A|1981-07-23|1985-07-02|Facet Enterprises, Inc.|Fuel pump with magnetic drive|
    US4457680A|1983-04-27|1984-07-03|Paget Win W|Rotary compressor|
    IT1287464B1|1996-07-29|1998-08-06|Giovanni Morselli|VOLUMETRIC ROTARY MACHINE|
    US6129067A|1997-11-28|2000-10-10|Riley; Thomas|Rotary engine|
    US8517706B2|2002-05-06|2013-08-27|Jerome R. Lurtz|Non-eccentric engine|
    US9394901B2|2010-06-16|2016-07-19|Kevin Thomas Hill|Pumping systems|
    RU2458251C2|2010-10-19|2012-08-10|Сергей Васильевич Алешин|Compressor|US10731701B2|2018-07-23|2020-08-04|Hamilton Sunstrand Corporation|High efficiency gear pump bearing assembly|
    CN108953147A|2018-07-28|2018-12-07|周信城|cam compressor|
    KR102311679B1|2020-03-11|2021-10-08|김찬원|A Vacium Self-priming Pump|
    法律状态:
    2016-11-30| PUE| Assignment|Owner name: FRANCO TOMMASINI, CH Free format text: FORMER OWNER: G.P.S. GREEN POWER SOLUTION SA, CH |
    2017-05-15| PUE| Assignment|Owner name: G.P.S. GREEN POWER SOLUTION SA, CH Free format text: FORMER OWNER: FRANCO TOMMASINI, CH |
    优先权:
    申请号 | 申请日 | 专利标题
    PCT/IT2013/000260|WO2015044969A1|2013-09-27|2013-09-27|Positive displacement gear pump|
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