EP2852760A1

EP2852760A1 - Pulsation-free positive displacement rotary pump

Info

Publication number: EP2852760A1
Application number: EP13726269.7A
Authority: EP
Inventors: Thierry Navarro; Florent Junod
Original assignee: Swissinnov Product SARL
Current assignee: Swissinnov Product SARL
Priority date: 2012-05-23
Filing date: 2013-05-02
Publication date: 2015-04-01
Anticipated expiration: 2033-05-02
Also published as: AU2013264969A1; BR112014028942A2; IN2014DN10632A; EP2852760B1; CN104641109B; WO2013175277A1; US20150147210A1; US9970436B2; KR20150018826A; JP2015517627A; CA2874380A1; CN104641109A

Abstract

The invention relates to a pump comprising two pistons placed in a rotor, situated in a stator forming two opposite parallel eccentric pumping chambers having at least one inlet port through which the fluid is drawn into at least one of the pumping chambers during the filling movement of at least one of the pistons and, subsequently, expelled from at least one of the pumping chambers, during the emptying movement of at least one of the pistons, to at least one outlet port, characterized by an inlet cavity in connection with the inlet port, an outlet cavity in connection with the outlet port and two port changeover transition zones situated between each side of the cavities.

Description

ROTARY PUMPS VOLUMETRIOUS WITHOUT PULSATION

The invention relates to a volumetric pump, preferably without pulsation, consisting of two rotary pistons for the precise and variable dispensing of liquid, medicine, food, detergent, cosmetic product, chemical compound or any other type of fluid, gel or gas.

The prior art

There are various motors and rotary piston systems as described in US Pat. No. 1,778,843, US Pat. No. 4,717,771 and US Pat. No. 7,442,196 whose operating principle consists in driving a rotor containing two cylinders and parallel pistons, eccentric in opposition under the effect of fuel combustion. contained in the cylinders.

In US1776843, the guide of the pistons is by bearings fixed to the ends of the pistons sliding along a cam placed on the inner wall of the stator and a second cam connected to the stator next to the rotor. The return motion of the pistons is achieved by moving the bearings along the two cams.

In US4177771, the guide of the pistons is by bearings fixed to the ends of the pistons sliding along the stator having an oblong shape. Pistons move radially as the rotor rotates. The return movement of the pistons can only be achieved by the coupling of two pairs of parallel pistons fixed to the rotor, each pair of which is offset by 180 ° with respect to the other and eccentric with respect to the axis of the piston. rotor rotation, so that the compression movement of the gases in a pair of pistons is ensured during the explosion of the gases in the other pair.

In the case of US Pat. No. 7,442,196, the pistons are guided by means of a circular cam on the stator in which the drive shafts of the connecting rods connected to the pistons slide. The return movement of the pistons is achieved by the eccentricity of the axis of rotation of the rotor relative to the axis of the stator.

Although these systems can potentially be adapted to function as a pumping system, a first problem encountered by these systems is that they consist of many parts that make their production and maintenance costs high for use in a medical or healthcare environment. for example, which must be cleaned or sterilized.

The second problem is that the principle of spring valves used by these systems for the dispenser is unsuitable for the production of pumping systems of injected plastic parts which is normally made using elastomeric gaskets.

The third problem is that these systems have a discontinuous alternating operating cycle which does not allow to obtain a pulsating flow rate in the case of their use as a pumping system.

A fourth problem encountered is that these systems are not feasible plastic injected parts for the production of inexpensive consumable fluid module pumps that can be discarded after use. Description of the invention

The present invention relates to a high performance pump composed of a reduced number of parts with a very low production cost for pumping and dosing liquids, viscous products or variable flow gases without pulsation. This invention solves the problems discussed above and allows for simplified development for the very large scale production of pumps with an element in contact with the interchangeable pumped fluid, preferably inexpensive disposable plastics.

The pump comprises two pistons, parallel in opposition, placed in two cylindrical cavities of a rotor rotating in a cylindrical stator, with at least one input port and at least one output port, having on its inner face a guide cam pistons and a housing preferably for a sealing element positioned between the rotor and the stator.

The principle of pumping consists of rotating the rotor placed inside the stator so as to axially move the pistons in the rotor via the cam located on the inner wall of the stator. The cam is dimensioned according to six segments, a short nominal fill segment, two short discharge segments with a flow rate lower than the nominal flow rate of the pump, a long discharge segment at the nominal flow rate of the pump and two valve switching segments between the inlet and outlet ports on each pumping chamber. During the phase of emptying a chamber at the rated flow rate of the pump, the other chamber switches from the output port to the input port, then fills up completely and switches from the input port to the output port, then the two chambers preferably preferably expel simultaneously to the output port at a reduced flow rate, the sum of which equals the nominal flow rate of the pump so that the output flow rate is preferably stable, continuous, uninterrupted and without pulsation. The switching system of the inlet and outlet ports to the pumping chambers is synchronously adapted to the movement of the pistons without additional element in order to achieve a high performance seal with a minimum of components.

The drive of the pump consists mainly of a support, a drive head and an actuator, preferably in the form of a motor. The pump is particularly well suited for low-cost production as it consists only of easily injectable plastic parts that can be assembled automatically.

Description of the drawings

The present invention will be better understood on reading the description of the examples given, purely by way of indication and in no way limiting, with reference to the appended drawings in which:

FIG. 1 is a view of one end of the stator

FIG. 2 is a view of the rotor placed inside the other end of the stator

FIG. 3 is an overview of the invention coupled to a motor assembly. FIG. 4 is an overall view of an engine with a support for fixing the invention.

FIG. 5 is a side exploded view of the elements constituting the invention

FIG. 6 is an internal exploded view of the elements constituting the invention.

FIG. 7a is a view of the front face of the invention

FIG. 7b is a side view of the invention

FIG. 7c is a longitudinal section along the line A-A of FIG. 7b

FIG. 7d is a longitudinal section along line BB of FIG. 7b FIG. 8 is a view of the rear face of the invention

Figure 8a is a longitudinal section along the line C-C of Figure 8

Figure 8b is a longitudinal section along the line D-D of Figure 8

FIG. 9 is a plan view of a piston

Figure 9a is a longitudinal section along line E-E of Figure 9

FIG. 10 is a top view of the stator with the pistons and the guide cam. FIG. 11 is a graph of the linear displacements of the pistons as a function of the angular displacement of the rotor.

Second variant

FIG. 12 is a view from above of a second variant of the invention

Figure 13 is a longitudinal section along the line A-A of Figure 12

Figure 14 is a longitudinal section along line B-B of Figure 12

FIG. 15 is a perspective view from below of the invention

FIG. 16 is an internal view of the stator of the invention

FIG. 17 is an internal view of the hood of the invention

Figure 18 is a view of the rotor of the invention

Figure 19 is a view of a piston of the invention

Fig. 20 is a view of a guide element of the invention

Third variant FIG. 21 is a view of an assembly of the third variant of the invention with drive and motor

Figure 22 is a perspective view of the top of the invention

FIG. 23 is a perspective view of the bottom of the invention

- Figure 24 is a side view of the set

FIG. 25 is a front view of the assembly

Figure 26 is a top view of the set

- Figure 27 is a longitudinal section along the line A-A of Figure 24

Figure 28 is a longitudinal section along the line B-B of Figure 26

- Figure 29 is a longitudinal section along the line C-C of Figure 26

FIG. 30 is a longitudinal section along line D-D of FIG.

FIG. 31 is a longitudinal section along the line E-E of FIG.

Figure 32 is a front view of the invention

- Figure 33 is a longitudinal section along the line F-F of Figure 32

FIG. 34 is a longitudinal section along the line G-G of FIG. 26

Fourth variant

FIG. 35 is a view of an assembly of the fourth variant of the invention with drive and motor

- Figure 36 is a front view of the set

Figure 37 is a side view of the assembly

- Figure 38 is a longitudinal section along the line A-A of Figure 36

FIG. 39 is a longitudinal section along line D-D of FIG. 36

Figure 40 is a longitudinal section along the line EE of Figure 37 FIG. 41 is a longitudinal section along the line FF of FIG. 37

According to Figures 1 and 2, the pump (1) consists of a stator (2) and a rotor (3) placed inside the stator (2). In FIGS. 3 and 4, the pump (1) is coupled to a motor (30) preferably via a drive head (31) and a holding support (34) for receiving the stator (2) of the pump (1). Pins (32, 32 ') placed on the drive head (31) housed in the hollow base (33) of the rotor (3) rotate the rotor (3) of the pump (1) when the it is coupled to the motor assembly (35).

In FIGS. 5 and 6, the stator (2) consists of a cam (10) placed on its inner face (2 '), a housing (1 1) receiving a sealing element (4), an input port (14) and an output port (16). The rotor (3) consists of two cavities (18, 18 '), preferably cylindrical, parallel, opposite and eccentric to the axis of rotation of the rotor (2), having notches (8, 8') placed respectively at the upper ends of the cavities (18, 18 ') and through holes (9,9') connecting each lower end of the cavities (18,18 ') with the inner face (3') of the rotor (3). Two pistons, preferably identical, (5,5 ') each consist of two circular seals (7,7'), a front channel (19) placed on the front face of the piston (5) in connection with a lateral channel (20) located between the two circular seals (7,7 ') and a guide element (6) placed at the lower end perpendicularly to the axis of the piston (5).

According to FIG. 7c, the pistons (5, 5 ') placed in the cavities (18, 18') of the stator (3) respectively form two parallel parallel eccentric pumping chambers (21, 21 ') 180 ° apart.

In FIGS. 7d and 14, the input cavity (13) in connection with the input port (14), the output cavity (15) in connection with the output port (16) and the two transition zones Switching port (17, 17 ') located between each side of the cavities (13, 15) are positioned on the stator (3) so as to correspond to the filling and emptying phases of the chambers (21, 21') according to the cam (10) . The guide elements (6,6 ') of the pistons (5,5') are placed perpendicularly in the cam (10) of the stator (2). According to Figure 8, the guide elements (6,6 ') are driven and held by the notches (8,8') of the rotor (3). In FIG. 8a, the sealing element (4) is placed between the stator (2) and the rotor (3).

According to Figures 10 and 1 1, the profile of the cam (10) of the stator (2) consists of six segments delimited by the points (50, 51, 52, 53, 54, 55). Each segment of the cam (10) preferably corresponds to one phase of the pumping sequence in the following manner; the low-flow discharge start phase is on the segment between the points (53,52), the nominal flow discharge phase is on the segment between the points (52,51), the end-of-drain phase at reduced flow is on the segment between the points (51,50), the switching phase of the output port (16) to the input port (14) is on the segment between the points (50,55) , the filling phase is on the segment between the points (55, 54) and the switching phase of the input port (14) to the output port (16) is on the segment between the points (54, 54), 53). Each segment of the cam is dimensioned so as to preferably obtain a linear displacement of the pistons (5,5 ') so that the nominal flow rate (60) at the pump outlet (1) is constant without pulsation. According to FIG. 11 and the previous ones, the linear displacements of the pistons (5,5 ') correspond to constant flow rates (61, 6Γ, 62, 62' 63, 63 '). The nominal flow rate (60) of the pump (1) as a function of the rotation angle of the rotor (3) corresponds to the sum of the reduced flow rates (61, 6Γ) of the pumping chambers (21.2 P) for an angle of rotation preferably between 0 and 45 °, at the nominal flow rate (62) of the chamber (21) for an angle preferably comprised between 45 ° and 180 °, to the sum of reduced flow rates (63, 63 ') of the pumping chambers (21, 21') for a rotation angle preferably comprised between 180 ° and 225 ° and at the nominal flow rate (62 ') of the chamber (21') for an angle comprised between 225 ° and 360 °.

When the rotor (3) rotates from 0 ° to 45 °, the pistons (5, 5 ') move along the reduced flow cam (61, 61'), which has the effect of simultaneously expelling the liquid from the chambers (21, 21 ') to the outlet port (16) via the front channels (19, 19'), the side channels (20, 20 ') of the pistons (5, 5') and the through holes (9,9 ') in connection with the outlet cavity (15). When the rotor (3) rotates from 45 ° to 75 °, the piston (5) continues to expel the liquid from the nominal flow chamber (21) (62). The piston (5 ') stops moving linearly and the lateral channel (20') via the through hole (9 ') is connected to the port switching transition zone (17') which closes the bedroom (21 '). When the rotor (3) preferably rotates from 75 ° to 150 °, the piston (5) continues to expel the liquid from the chamber (21) at a nominal flow rate (62). The piston (5 ') moves linearly in the opposite direction which has the effect of sucking the liquid in the chamber (2) from the inlet port (14) via the front channel (19'), the side channel ( 20 ') and the through-hole (9') in connection with the inlet cavity (13).

When the rotor (3) preferably rotates from 150 ° to 180 °, the piston (5) continues to expel the liquid from the chamber (21) at a nominal flow rate (62). The piston (5 ') stops moving linearly and the lateral channel (20') via the through hole (9 ') is connected to the port switching transition zone (17) which closes the chamber (2 Γ). When the rotor (3) preferably rotates from 180 ° to 225 °, the pistons (5, 5 ') move along the reduced flow cam (63,63'), which has the effect of simultaneously expelling the chamber liquid (21,21 ') to the outlet port (16) via the front channels (19, 19'), the side channels (20,20 ') of the pistons (5,5') and the passage (9,9 ') in connection with the outlet cavity (15).

When the rotor (3) rotates from 225 ° to 255 °, the piston (5 ') continues to expel the liquid from the chamber (2 Γ) at a nominal flow rate (62'). The piston (5) stops moving linearly and the lateral channel (20), via the through hole (9), is connected to the port switching transition zone (17 ') which closes the chamber (21). ). When the rotor (3) rotates from 255 ° to 330 °, the piston (5 ') continues to expel the liquid from the chamber (21') at a nominal flow rate (62 '). The piston (5) moves linearly in opposite directions which has the effect of sucking the liquid in the chamber (21) from the inlet port (14) via the front channel (19), the side channel (20) and the through hole (9) in connection with the inlet cavity (13).

When the rotor (3) preferably rotates from 330 ° to 360 °, the piston (5 ') continues to expel the liquid from the chamber (21') at a nominal flow rate (62 '). The piston (5) stops moving linearly and the lateral channel (20), via the through hole (9), is connected to the port switching transition zone (17) which closes the chamber (21) .

When the rotor (3) is turned 360 ° relative to the stator (2) it is in the 0 ° position, which corresponds to a complete pump cycle of the pump (1). Description of a second variant of the invention

According to Figures 13 and 17, a cover (70) is placed opposite the stator (2) so as to maintain the rotor (3) between the cover (70) and the stator (2). The cover (70) is held on the stator (2) preferably using at least one clip (71) and a clip (72). The tightening of the rotor (3) in the stator (2) can thus be ensured by the cover. In a variant, not shown, the cover (70) provides pre-tightening and clamping in operation is performed by an external locking member bearing on the cover (70) and the stator (2).

Guiding elements (76,76 '), preferably in the form of pins, are placed inside the holes (75,75') of the pistons (5,5 ') so as to guide the pistons (5,5'). ) along the cam (10) of the stator (2) and the cam (10 '), symmetrical to the cam (10), placed on the inside of the cover (70). The guiding elements (76,76 ') are thus perfectly guided symmetrically at their ends making the displacements of the pistons (5,5') more efficient and ensuring a better resistance to the forces when the pump rotates at high speed or delivers at high speed. High pressure. The guide members (76,76 ') freely rotate within the holes (75,75') of the pistons (5,5 ') so as to reduce friction with the cam (10) and the cam (10').

According to FIG. 16, the input and output ports (14, 16) are optionally placed perpendicularly to the axis of rotation of the rotor (3).

Description of a third variant of the invention According to FIGS. 21, 22 and 26, the assembly (80) is composed of a motor (30) fixed to a support (81) receiving the pump (1) held on the support (81) by fastening elements (82,82 ') preferably in the form of clips. The carrier (81) is adapted to receive at least one air or pressure sensor (83) preferably attached near the inlet (14) or outlet (16) port. The sensor (83) can receive a tube (85) in the housing (84) to detect air bubbles or to measure the pressure at the inlet (14) or the outlet (16) of the pump (1). ). The fasteners (82, 82 ') may be integral with the pump (1), the carrier (81), or a combination of both. The rotor (3) is driven by the motor shaft (89).

According to FIGS. 7d, 23, 28, 29 and 31, the rotor (3) is held in abutment against the sealing element (4) by means of at least one return element (90), for example a spring or other means when the pump (1) is not connected to the support (81) and can be moved axially towards the return member (90) by pressing on the lower end (86) of the rotor (3) ). During axial displacement, the rotor (3) is no longer in contact with the sealing element (4) which creates a controlled channel or leak (not shown) between the cavities (13, 15) for connecting the input and output ports (14, 16) directly. Sealing towards the outside is ensured by the sealing elements 98 and 99. This function is particularly adapted in the procedures requiring to circulate the fluid through the pump (1) and the inlet and outlet tubes ( not shown) connected to the input and output ports (14, 16) without the aid of an external drive. This type of procedure is commonly used in a hospital setting when a pump is turned on to purge the air by gravity contained in the tubes or pipes connected to the pump (1) before connecting it to the head of the pump. drive (31) or support (81). Similarly, it may be necessary to purge the fluid contained in the tubes or pipes after use of the pump or when the drive is inoperative. The seal (97) optional, improves the guidance of the rotor. The return element (90) can be adapted so that the function is reversed and the rotor (3) must be pulled in the direction opposite to the return element (90) to bear on the element sealing (4).

According to Figures 7c, 7d and 33, the cam (10) is adapted to be able to position a guide member (6 or 6 ') in a groove (101) preferably located within the cam (10). When a guide element (6 or 6 ') is placed at the bottom of the groove (101), the associated piston (5 or 5') is held in the upper position in the pumping chamber (21 or 2Γ) in order to have the minimum volume. By placing the other guide element (6 'or 6) also in the up position on the cam (10), the second pumping chamber (2 Γ or 21) is maintained with the minimum volume. It is then possible to completely purge the fluid, such as air, contained in the internal conduits of the input and output ports (14, 16) and the cavities (13, 15) and switching transition zones ( 17, 17 ') by pressing or pulling on the lower end (86) of the rotor (3), as previously explained. This function is particularly suitable when it is necessary to completely purge the fluid in the pump before or after its use. In the case, where the two chambers are not entirely empty, by placing the pistons (5,5 ') in the high position, the residual fluid contained in the chambers (21,2) can be dangerous for example when an intravenous infusion and that the unpurchated air causes an embolism.

According to FIGS. 23, 30, 31 and 34, the stator (2) is adapted to receive two flexible elements (87, 87 '), preferably in the form of silicone or elastomer membranes, in connection respectively with the ports of inlet and outlet (14, 16) and the pumping chambers (21, 21 ') via the channels (93 and 93'). Each channel (93,93 ') is connected at its other end respectively to the cavities (94,94') located between the stator (2) and the flexible elements (87,87 '). When the pump (1) is fixed on the support (81), each flexible element (87,87 ') forms with the support (81) two cavities (95,95') each having respectively a connecting channel (102, 102 ') placed in the support (81).

During the operation of the pump (1) the pressure variations in the pumping chambers (21, 21 ') respectively deform the flexible elements (87, 87') which transmit the pressure of each cavity (94, 94 ' ) respectively to the cavities (95,95 '). It is then possible to measure the pressure at the inlet and the outlet of the pump by placing two pressure sensors (not shown) at the outer ends of the channels (102, 102 '). The flexible elements (87,87 ') provide insulation and sealing between the internal fluid circuit of the pump and the outside, while allowing measurement of pressure variations at the inlet and the outlet pump. This system is particularly well suited for measuring occlusions or leaks at the inlet or outlet of the pump without having to connect pressure sensors to the external tubings of the pump. The integration of flexible elements (87,87 ') in the pump (1) reduces the overall size of the system, which is extremely important for example for portable pumps especially in the medical field.

Description of a fourth variant of the invention

According to Figures 35, 38 and 39, the assembly (120) is composed of a motor (30) fixed on a support (81) receiving the stator (2). The rotor (3) is positioned inside the stator (2) so that the sealing element (4) is held between the rotor (3) and the stator (2). The cam (10) located inside the support (81) is adapted to receive at least one pair of bearings (123, 123 ') respectively fixed to the guide elements (6, 6') in order to reduce friction and wear of the cam (10) and the guide elements (6,6 '). A second pair of bearings (124, 124 ') respectively fixed to the guide elements (6, 6') makes it possible to reinforce the alignment of the guide elements (6, 6 ') when it is necessary to deliver doses. very precise fluids and the most perfect linear flow possible. The rotor (3) can be optionally guided in the stator (2) and the support (81) by bearings or bearings

The previously described pumping principle is reversible by rotating the rotor in the other direction.

The angular values defined above are given by way of example and may be different depending on the dimensioning of the cam or the desired flow curve. The reduced flow rates (61, 61 ', 63, 63') are preferably equivalent to half the nominal flow rate of the pump.

The cam can be adapted to obtain a pulsed or semi-pulsed flow.

In another variant, not illustrated, the housing (1 1) and the sealing element (4) can be placed on the inner face of the rotor (3). In another variant, not illustrated, the cavities (13, 1 5) and switching transition zones (17, 17 ') may be perpendicular to the axis of rotation of the pump. In this case, the sealing element is preferably placed at the periphery of the rotor of the pump.

In another variant not shown, the rotor may be adapted to review a magnetic element so as to be rotated by means of a magnet or other external electromagnetic element. The pump can thus be coupled to a drive without contact. This variant is particularly suitable in the case where the pump is implanted under the skin or in the body and must be operated from the outside.

In another variant not shown, the cover can be adapted to receive the pump input and output ports. The sealing between the moving parts is preferably achieved by an elastomer, an overmolded seal or any other sealing element. However, it is possible to realize the pump without seal between the stator or the cover and the rotor by adjustment for example. The elements constituting the pump are preferably plastic and disposable. The pump can be sterilized for dispensing food or medicine for example. The choice of materials, however, is not limited to plastics.

Although the invention is described according to several embodiments, there are other variants that are not presented. The scope of the invention is therefore not limited to the embodiments described above.

Claims

claims

1. A pump comprising, two pistons (5,5 ') placed in a rotor (3), located in a stator (2) forming two parallel, eccentric opposite pumping chambers (21, 21') having at least one port inlet (14) through which the fluid is sucked into at least one of the pumping chambers (21, 21 ') during the filling movement of at least one of the pistons, and then expelled from at least one of the pumping chambers during the movement of at least one of the pistons towards at least one exit port (16), characterized by an inlet cavity (13) connected to the input port (14), with an exit cavity (15) in connection with the output port (16) and two port switching transition areas (17, 17 ') located between each side of the cavities (13, 15).

2. Pump according to claim 1, the output flow rate is continuous without pulsation.

3. Pump according to claim 1, wherein the stator (2) comprises a cam (10) on its inner face (2 ').

4. Pump according to claim 1, whose pistons (5,5 ') comprise guide elements (6,6') placed perpendicularly in the cam (10) of the stator (2).

5. Pump according to claim 1, whose pistons (5,5 ') comprise front channels (19,19') in connection with side channels (20,20 ').

6. Pump according to claim 1, a sealing member (4) is placed between the stator (2) and the rotor (3).

7. Pump according to claim 1, the sum of reduced flow rates (61, 61 ') and (63,63') correspond to the nominal flow (60).

8. Pump according to claim 1, wherein the two pumping chambers (21, 21 ') expel simultaneously to the output port (16) during the partial rotation of the rotor (3).

9. Pump according to claim 1, a cover (70) is placed vis-à-vis the stator (2).

10. Pump according to claim 9, whose cover (70) has on the inside a cam (10 ') symmetrical to the cam (10).

1. A pump according to claim 3, the profile of the cam (10) is composed of six segments.

12. Pump according to claim 4, whose guide elements (6,6 ') are driven and held by the notches (8,8') of the rotor (3)

13. Pump according to claim 1, wherein the seal between the moving parts is made with at least one elastomer.

14. Pump according to claim 1, whose parts are plastic and disposable

15. Pump according to claim 1, having at least one flexible element in connection with the input or output port.

16. Pump according to claim 1, wherein the rotor can be moved axially.