EP2531728A1

EP2531728A1 - Pump

Info

Publication number: EP2531728A1
Application number: EP11701358A
Authority: EP
Inventors: Markus Müller
Original assignee: Yasa Motors Poland Sp zoo
Current assignee: Yasa Motors Poland Sp zoo
Priority date: 2010-02-04
Filing date: 2011-01-24
Publication date: 2012-12-12
Also published as: DE102010006929B4; DE102010006929A1; WO2011095287A1; US9109585B2; US20120328459A1

Abstract

The invention relates to a pump (1) for conveying a fluid from an intake region (2) to a discharge region (3), which pump comprises a housing (4) as well as at least one rotor (6) that is arranged in the housing (4) so as to be rotatable about an axis of rotation (5) and can be driven by a drive element. In order to achieve a high degree of efficiency, the pump according to the invention is characterised in that the rotor (6) has a bore (7) passing therethrough, a piston element (8) that is able to move in the direction of the longitudinal axis (L) of the bore is arranged in the bore (7), and a number of magnets (9, 9', 9'', …) or an annular magnet is fixedly arranged in the housing (4). The magnets or the annular magnet exert(s) an attractive force on the piston element (8), wherein the magnets (9, 9', 9'', …) or the annular magnet are/is positioned in the housing (4) such that, on rotation of the rotor (6) about the axis of rotation (5), the piston element carries out an oscillating movement (O) in the bore (7) as a consequence of the magnetic force of attraction.

Description

pump

The invention relates to a pump for conveying a fluid from a suction region in a delivery region, which has a housing and at least one rotatable in the housing about a rotational axis arranged rotor, which can be driven by a drive element.

Pumps of this type are well known in the art. They are used for example in heating systems to pump water through the heating circuit. In most cases, centrifugal pumps are used in particular for the mentioned application.

However, these pumps have proven to be disadvantageous in terms of energy efficiency. At typical speed and flow rate, the hydraulic efficiency is usually not more than 35%. The reason for this is the recirculation with which centrifugal pumps work to achieve the necessary pressure build-up. The resulting losses have a disproportionate effect with a small pump size, as is typical for applications in the heating industry.

From an economic point of view, it is still necessary to be able to produce the pump cost, since it is needed in very large quantities. The invention is therefore based on the object, a pump of the type mentioned in such a way that the hydraulic efficiency can be increased, with a cost-effective manufacturing capability should exist. Thus, the pump should be used advantageously, but not exclusively, in the field of heating construction.

The solution to this problem by the invention is characterized in that the rotor is penetrated by a bore, that in the bore a piston element is arranged, which can move in the bore longitudinal axis, and that fixed in the housing, a number of magnets or a ring magnet is arranged, wherein the magnet or the ring magnet on the piston member exerts a magnetic attraction, wherein the magnets or the ring magnet is placed in the housing or is such that upon rotation of the rotor about the axis of rotation, the piston member due to the magnetic attraction in the bore exerts an oscillating motion.

Accordingly, the magnets move the piston element during rotation of the rotor in the direction of the longitudinal axis of the bore; this oscillating movement is used to convey the fluid and pressurize it.

The piston element is preferably a ball. The piston element is preferably a magnet or it has at least one magnet.

The piston element (ie preferably the ball) is preferably tolerated in the bore, that in the translational displacement of Piston member displaced in the bore fluid located in the bore out of the bore or is sucked into the bore.

The bore extends advantageously in the rotor perpendicular to the axis of rotation of the rotor.

Between the housing and the rotor a seal is preferably arranged or formed at two opposite points of the rotor. The seal is preferably formed by a constriction between the rotor and the housing. Between the sealing points and the intake region, a flow channel for fluid to be sucked can be formed. Accordingly, a flow channel for fluid to be dispensed can be formed between the sealing points and the delivery area. The magnets which control the movement of the piston member in the bore are preferably arranged along a closed cam track in the housing; Preferably, the curved path is a circular path. As an alternative to a number of discrete magnets, a ring magnet can also be used. The magnets or the ring magnet are or is preferably designed as a permanent magnet / e.

The diameter of the bore is preferably an amount between 0.05 mm and 0.3 mm, preferably between 0, 1 mm and 0.2 mm, greater than the diameter of the piston member, in particular the ball.

The inner surface of the bore is particularly preferably provided with a hard material layer in order to increase the wear resistance of the bore surface. It can be provided in the rotor and a plurality of, in particular offset over the circumference arranged holes in which respective piston elements are arranged. The proposed design of the pump has the consequence that a much higher hydraulic efficiency can be achieved than is the case with centrifugal pumps. By the proposed displacement principle, an efficiency of up to 80% can be achieved. The relatively simple structure also allows cost-effective production, so that even large lots of pumps can be produced economically.

In the drawing, an embodiment of the invention is shown. Show it:

1 shows schematically a pump according to the invention, the pump being sketched in a sectional view and showing only the components which are important in connection with the invention,

Fig. 2 shows schematically the pump of FIG. 1 during a first

3 shows schematically the pump according to FIG. 1 during a second process step of the pumping operation

Process step of the pumping process,

Fig. 4 shows schematically the pump of FIG. 1 during a third

Process step of the pumping process and 5 schematically shows the pump according to FIG. 1 during a fourth process step of the pumping process. In Fig. 1, a pump 1 is outlined, with only the relevant here essential components are shown. The pump 1 works according to the displacement principle. It has a housing 4 which extends in a conveying direction F, in which a fluid, for. As water is promoted. In this case, the housing 4 extends substantially from a suction region 2 to a delivery region. In the suction area 2, fluid is sucked into the pump 1 and pressurized, the fluid then being discharged in the discharge area 3 under increased pressure.

The central component of the pump 1 is a rotor 6, which can rotate about an axis of rotation 5, which is perpendicular to the plane in the figures. Not shown is a motor with which the rotor 6 can be rotated.

The rotor 6 has a through hole 7, which extends transversely and centrally through the rotor 6 and which is perpendicular to the axis of rotation 5. Accordingly, the bore 7 extends in the direction of the bore longitudinal axis L. In the bore 7, a piston member 8 is arranged in the form of a ball. In the ball 8, a permanent magnet is integrated.

Above the center of the rotor 6, a number of magnets 9, 9 ', 9 ", ... stationary arranged in the housing 4, in such a way that the magnets 9, 9', 9", ... along a circular path (s Reference numeral 14 in Figures 2 to 5) are arranged. The circular diameter of this circular path is about half the diameter of the rotor 6. The magnets 9, 9 ', 9 ", ... are - like the ball 8 - designed as permanent magnets. The magnets 9, 9 ', 9 ", ... exert on the ball 8 a magnetic attraction, ie the ball 8 is attracted by the magnets 9, 9', 9", .... In this case, of course, the magnet 8, 9 ', 9 ", ..., which is closest to the ball 8, exercises the dominant attractive force.

The rotor 6 has in its uppermost and lowermost region only a small distance from the wall of the housing 4, which is shown greatly exaggerated in Fig. 1. Therefore, there is a sealing gap 10 or 1 1 at the two locations mentioned, so that hardly any fluid can flow from the intake area 2 to the discharge area 3 here. Rather, the sites marked 10 and 11 are to be regarded as sealed sites.

This results in a flow channel 12 for sucked fluid from the intake region 2 to the rotor 6 and a flow channel 13 for the fluid to be delivered from the rotor 6 to the delivery region 3.

Moves the ball 8 translationally in the bore back and forth, ie it performs an oscillating movement O, it comes out of the bore 7 due to the relatively close (match) fit between ball diameter and bore diameter to promote the fluid. As will be seen later on, in the left-hand region of the pump 1, fluid is sucked off from the intake region 2 via the flow channel 12 in the counterclockwise direction when the rotor 6 rotates and is required in the flow channel 13 to the delivery region 3. The outer diameter d of the ball is preferably about 0, 1 to 0.2 mm smaller than the diameter D of the bore. 7 In FIGS. 2 to 5, the sequential sequence of the pumping process is outlined. The process step according to FIG. 5 is followed again by that according to FIG. 2 and the process is repeated accordingly. The total of 16 discrete magnets 9, 9 ', 9 ",..., To be recognized in FIG. 1 are not shown in FIGS. 2 to 5 for the sake of clarity, but only the circular path 14 along which the magnets 9, 9', 9 ", ... are arranged. In a first process step, the rotor 6 is shown in FIG. 2 in a starting position, ie the bore 7 extends in the longitudinal direction of the pump 1 from the intake 2 to the delivery area 3. The ball 8 closes the bore 7, the ball 8 from the next magnet. 9 * (see Fig. 1) is tightened and held in position due to the magnetic force.

For pumping fluid, the rotor is driven counterclockwise by the drive means, not shown.

FIG. 3 shows, for a second process status, that the rotor 6 has been rotated by the angle in comparison to the basic position according to FIG. 2. The magnets 9, 9 ', 9 ", ... pulled the ball 8 further in the direction of the bore longitudinal axis L, so that now a translational displacement x (see FIG L, which is located in the region of the bore above the ball 8, is therefore pushed out in the direction of the discharge area 3, while the growing volume of the bore 7 between the bottom left entry into the bore 7 and the ball 8 fluid from the intake 2 is sucked into the bore 7. The flow of fluid is indicated by arrows. Upon further rotation - as shown in FIG. 4 for a third process status upon rotation of the rotor 6 with respect to the initial position shown in FIG. 2 by the angle ß - the ball 8 of the magnets 9, 9 ', 9 ", ... in the direction Hole end pulled until in the position shown in Fig. 4, the magnet 9 ** (see Fig. 1) holds the ball 8 in position.

Upon further rotation by the angle γ of FIG. 5 for a fourth process status, the ball 8 is moved back again in the bore 7, since the ball 8 in turn follows the course of the circular path 14 and the corresponding magnet (in Fig. 5 from about Magnets 9 ***, see Fig. 1) is held in position. As a result of the return movement of the ball 8, fluid is drawn in from the suction region 2 via the flow channel 12 and discharged from the bore hole located at the bottom right under increased pressure via the flow channel 13 to the delivery region 3 from the bore 7. The flow of the fluid is again indicated by arrows.

Upon further rotation of the rotor 6 (until reaching an angle γ of 180 °), the initial state shown in FIG. 2 is reached again and the process according to FIGS. 2 to 5 is repeated.

As is apparent from the explained operation, the oscillation frequency of the ball 8 in the bore 7 corresponds to twice the rotational frequency of the rotor 6.

Since no noteworthy fluid flow can take place via the sealing gaps 10, 11, which are shown at great exaggeration, a significant pressure increase is achieved in the described pumping process. Of the Pressure build-up can easily reach up to 0.5 bar, but for the purpose of application in heating construction, hardly more than a pressure build-up of 0.2 to 0.3 bar is required. In normal operation, maximum oscillation speeds of the ball 8 are achieved in the bore 7 between 0.5 and 2 m / s.

Since the ball 8 thus oscillates in the bore 7 at a relatively high frequency, a low-friction and low-wear running of the ball in the bore is important. Accordingly, the cylindrical inner surface of the bore 7 is provided with a hard material layer, so that there is a high abrasion resistance.

At the same time can be achieved by appropriate choice of the coating and the ball, a low coefficient of friction between the ball and the bore surface.

In the ball 8 a magnet of rare earth is arranged in the embodiment. In the exemplary embodiment, discrete magnets 9, 9 ', 9 ", ... are provided, and of course a ring magnet can also be used.The use of a ring magnet can prove more favorable and in particular make the guiding properties of the piston element more uniform. REFERENCE LIST;

1 pump

2 intake area

3 delivery area

4 housing

5 axis of rotation

6 rotor

7 hole

8 piston element (ball)

9 magnet / ring magnet

9 'magnet

9 "magnet

10 seal / sealing gap

1 1 seal / sealing gap

12 flow channel

13 flow channel

14 curved path (circular path)

F conveying direction

L bore longitudinal axis

O oscillating movement

D Diameter of the hole

d diameter of the piston element (the ball)

Claims

claims:

1. pump (1) for conveying a fluid from a suction region (2) in a delivery region (3) which has a housing (4) and at least one rotor (6) which is rotatable about a rotation axis (5) in the housing (4) , which can be driven by a drive element, characterized in that the rotor (6) is penetrated by a bore (7), that in the bore (7) a piston member (8) is arranged to move in the bore longitudinal axis (L) can, and that in the housing (4) fixed a number of magnets (9, 9 ', 9 ", ...) or a ring magnet is arranged, wherein the magnet or the ring magnet on the piston member (8) exert a magnetic attraction or , wherein the magnets (9, 9 ', 9 ", ...) or the ring magnet are placed in the housing (4) such that upon rotation of the rotor (6) about the axis of rotation (5) the piston element due to the magnetic attraction in the bore (7) an oscillating movement (O) exerts.

Pump according to claim 1, characterized in that the piston element (8) is a ball.

Pump according to claim 1 or 2, characterized in that the piston element (8) is a magnet or has a magnet.

Pump according to one of claims 1 to 3, characterized in that the piston element (8) is so tolerated in the bore (7) that in the translational displacement of the piston element (8) in the bore (7) in the bore (7 ) Fluid is displaced out of the bore (7) out.

Pump according to one of claims 1 to 4, characterized in that the bore (7) in the rotor (6) perpendicular to the axis of rotation (5) of the rotor (6).

Pump according to one of claims 1 to 5, characterized in that between the housing (4) and the rotor (6) at two opposite points of the rotor (6) each have a seal (10, 1 1) is arranged or formed.

7. Pump according to claim 6, characterized in that the seal (10, 1 1) by a constriction between the rotor (6) and housing (4) is formed.

8. A pump according to claim 6 or 7, characterized in that between the sealing points (10, 1 1) and the suction region (2) a flow channel (12) is formed for fluid to be sucked.

9. A pump according to claim 6 or 7, characterized in that between the sealing points (10, 1 1) and the discharge area (3) a flow channel (13) is formed for the fluid to be dispensed.

10. Pump according to one of claims 1 to 9, characterized in that the magnets (9, 9 ', 9 ", ...) along a curved path (14) in the housing (4) are arranged.

1 1. A pump according to claim 10, characterized in that the curved path (14) is a circular path.

Pump according to one of claims 1 to 1 1, characterized in that the magnets (9, 9 ', 9 ", ...) are permanent magnets or that the ring magnet is a permanent magnet.

Pump according to one of claims 1 to 12, characterized in that the diameter (D) of the bore (7) by an amount between 0.05 mm and 0.3 mm, preferably between 0.1 mm and 0.2 mm, larger is as the diameter (d) of the piston member (8), in particular the ball (8).

14. Pump according to one of claims 1 to 13, characterized in that the inner surface of the bore (7) is provided with a hard material layer.