EP2681452B1 - Controllable coolant pump - Google Patents

Description

The invention relates to a controlled via a pulley controllable coolant pump for internal combustion engines.

In the course of the continuous optimization of internal combustion engines in terms of emission and fuel consumption, it is important to bring the engine after the cold start as quickly as possible to the operating temperature.

This minimizes both the friction losses (as the oil temperature decreases, the viscosity of the engine oil and thus the friction on all oil-lubricated components) reduces the emission values (since the catalysts only become effective after the so-called "light-off temperature", does the period until reaching this temperature be affected significantly the exhaust emissions) and also significantly reduces fuel consumption.

A very effective measure for engine heating is the "standing water" or the "zero leakage" during the cold start phase, in which the cylinder head must not be flowed through by coolant, thereby bringing the exhaust gas temperature very quickly to the desired level.

In this context, vehicle manufacturers would like leakage flows of less than 0.5 l / h ("zero leakage").

The studies on the fuel consumption of internal combustion engines in motor vehicles have also shown that a consistent thermal management (ie those measures which lead to an energetically and thermomechanically optimal operation of an internal combustion engine) can save about 3% to 5% fuel.

In the prior art, therefore, the Applicant both in the DE 10 2005 004 315 B4 , in the DE 10 2005 062 200 B3 as well as in the WO 2009/143832 A2 prescribed by the crankshaft of the internal combustion engine via pulleys controllable coolant pumps, which allow an active control of the coolant flow rate, on the one hand by "zero leakage" to ensure optimum heating of the engine and on the other hand after the heating of the engine (ie in "continuous operation") To influence the engine temperature so that both the pollutant emission, as well as the friction losses and at the same time also the fuel consumption can be significantly reduced in the entire working range of the engine.

In these solutions, a ring-shaped valve slide displaceably mounted in the pump housing in the direction of the shaft axis of the pump shaft is arranged with an outer cylinder which variably covers the outflow region of the impeller, which counter to the spring force of return springs either as in the solution according to the DE 10 2005 004 315 B4 proposed, electromagnetically, that is, by means of a solenoid arranged in the pump housing, which acts on a rigidly connected to the valve slide armature, or, as in the DE 10 2005 062 200 B3 proposed, by means of a pneumatically or hydraulically actuated actuator (which acts hydraulically on the valve slide rigidly arranged, guided in the pump housing piston rods) can be linearly displaced.

This arrangement of a guided, linearly displaceable, the outflow of the impeller variable overlapping valve spool is a very compact, simple and robust solution which ensures high reliability and high reliability.

The disadvantage, however, that the production and assembly of the in the DE 10 2005 004 315 B4 as well as in the DE 10 2005 062 200 B3 presented designs is very expensive, since most of the functional assemblies of this vg. Solutions are not standardized, and therefore must be made separately for each pump size.

When installing an electromagnetically actuated coolant pump as well as in the DE 10 2005 004 315 B4 above-described design, for example, in the vicinity of the turbocharger is necessarily cooling the solenoid (and thus a relatively large "space") required because otherwise the solenoid would be destroyed even at temperatures above 120 ° C.

For this necessarily required relatively large "space", either for the according to the DE 10 2005 004 315 B4 arranged in the pump housing solenoid, or according to the DE 10 2005 062 200 B3 arranged in the pump housing hydraulic or pneumatic actuators and their connecting lines results in a further disadvantage, which is diametrically opposed to the often very limited, available in the engine compartment "installation space" for the controllable coolant pump.

In order now even in unfavorable thermal boundary conditions, such as in the vicinity of the turbocharger, or even with very limited installation space a manufacturing and assembly technology simple, cost-effective, "standardizable" for different pump sizes, optimally exploiting the available space in the engine compartment space effective operation of the To ensure valve spool at high volumetric efficiency was by the applicant in the meantime also tried and tested, in the WO 2009/143832 A2 disclosed solution in which a hydraulic actuation of the valve spool via a provided with a return spring in the form of a compression spring piston pump, which is mechanically driven by an impeller arranged on the swash plate, is realized. In connection with a regulation according to the invention of the Piston pump "pumped volume flow" is this solution to a compact, very easy and inexpensive to be incorporated into the engine management, manufacturing and assembly technology simple and inexpensive to produce, robust and reliable solution.

A disadvantage of this solution, however, is that this design works too sluggish due to the return pump equipped with a return spring, and therefore is not suitable for high speed applications.

Also, the piston pump integrated in the pump housing from today's point of view requires too long a length expansion of the pump housing, with too many components and too high manufacturing and assembly costs.

The invention is therefore based on the object to develop a driven via a pulley controllable coolant pump (with valve slide), which eliminates the aforementioned disadvantages of the prior art, on the one hand by "zero leakage" ensures optimum heating of the engine and also on the other hand the engine warming can influence the engine temperature in continuous operation so accurately that the pollutant emission as well as the friction losses and the fuel consumption can be significantly reduced in the entire working range of the engine and even in unfavorable thermal boundary conditions, such as in the vicinity of the turbocharger, or even with very limited installation space for the coolant pump in the engine compartment with very low drive power reliable actuation of the valve spool, even in case of failure of the regulation further functioning of the coolant pump (fail-safe) ensures you rch a manufacturing and assembly technology very simple, cost-effective, "standardizable" for different pump sizes, characterized in their length very short design, which optimally exploits the available space in the engine compartment, and also ensures high reliability and reliability at high volumetric efficiency, no factory air-free Filling requires and can also be easily and inexpensively integrated into the engine management.

According to the invention, this object is achieved by a driven via a pulley controllable coolant pump for internal combustion engines according to the features of the independent claim of the invention.

Advantageous embodiments, details and features of the invention will become apparent from the dependent claims and the following description of the in conjunction with seven representations of the inventive solution.

Figur 1 :

die erfindungsgemäße regelbare Kühlmittelpumpe im Schnitt in der Seitenansicht;

Figur 2 :

die erfindungsgemäße regelbare Kühlmittelpumpe gemäß Figur 1 im Teilschnitt bei A - A, am Ende der "Einströmphase" kurz vor Beginn der Verdichtungsphase durch die Exzenterbuchse 27;

Figur 3 :

die erfindungsgemäße regelbare Kühlmittelpumpe gemäß Figur 1 im Teilschnitt bei A-A, zu Beginn der "Einströmphase";

Figur 4 :

die Einzelheit B der erfindungsgemäße regelbare Kühlmittelpumpe gemäß Figur 1;

Figur 5 :

Schnitt bei C-C in der Einzelheit B mit einer möglichen Bauform der erfindungsgemäßen regelbaren Kühlmittelpumpe gemäß Figur 4;

Figur 6 :

die Einzelheit B der erfindungsgemäßen regelbaren Kühlmittelpumpe gemäß Figur 1;

Figur 7 :

Schnitt bei D-D in der Einzelheit B mit einer weiteren möglichen Bauform der Einzelheit B der erfindungsgemäßen regelbaren Kühlmittelpumpe gemäß Figur 6.

It show the following:

FIG. 1:

the controllable coolant pump according to the invention in section in the side view;

FIG. 2:

the controllable coolant pump according to the invention according to FIG. 1 in partial section at A - A, at the end of the "inflow phase" shortly before the start of the compression phase through the eccentric bushing 27;

FIG. 3:

the controllable coolant pump according to the invention according to FIG. 1 in partial section at AA, at the beginning of the "inflow phase";

FIG. 4:

the detail B of the controllable coolant pump according to the invention according to FIG. 1 ;

FIG. 5:

Section at CC in the detail B with a possible design of the controllable coolant pump according to the invention according to FIG. 4 ;

FIG. 6:

the detail B of the controllable coolant pump according to the invention according to FIG. 1 ;

FIG. 7:

Section at DD in the detail B with a further possible design of the detail B of the controllable coolant pump according to the invention according to FIG. 6 ,

In these in the FIGS. 1 to 7 illustrated designs of the controllable coolant pump according to the invention is in a pump housing 1, with a mounted in / on the pump housing 1 in a pump bearing 2, driven by a pulley 3 pump shaft 4, on a free, flow-side end of this pump shaft 4 rotatably mounted impeller 5, a pressure-actuated , spring loaded by a return spring 6, control slide 7 with a Ausströmbereich of the impeller 5 variably overlapping outer cylinder 8, arranged in a pump housing 1 between the impeller 5 and the pump bearing 2 in a seal holder 9 shaft seal 10, a arranged on the pump housing 1 working housing 11 in which a solenoid valve 12 is arranged, wherein the inlet opening to a pressure channel 13 and to the outflow opening into the pump interior 14 recirculating passage 15 leads.

It is advantageous in this context that in the impeller 5, a vane bushing 42 is arranged, which reduces the manufacturing and assembly costs while increasing the reliability of the coolant pump.

Is essential to the invention that in the pump interior 14 on the pump housing 1 a together with the pump housing 1, a pressure chamber 16 forming spring plate 17 is arranged, on which the return spring 6 abuts, and on the outer radius of a slider inner seal 18 is arranged such that this inside of the outer cylinder 8 of Regulating slide 7 is applied, at the same time in the pump housing 1, an outside of the outer cylinder 8 of the Regulating slide 7 fitting slide outer seal 19 is arranged such that the outer cylinder 8 of the control slide 7 can be moved variable at pressure buildup in the pressure chamber 16 against the spring force of the return spring 6 along the Ausströmbereiches of the impeller 5. It is characteristic that in the pump interior 14 between the impeller 5 and the contact area of the spring plate 17 on the pump housing 1 rotatably in the pump housing 1 through the spring plate 17 projecting through, with a closed pump hole 14 closed blind bore 20 provided pivot cylinder 21 is arranged, the open Bore end 22 opens into the pressure channel 13, and at the opposite end, a Kolbenanlagesteg 23 is arranged, wherein rotatably mounted on the pivot cylinder 21, a working piston 24 is arranged with a Kolbendurchlassbohrung 25, the Kolbendurchlassbohrung 25 arranged in the region of the Kolbendurchlassbohrung 25 in the pivot cylinder 21 Through hole 26 opens into the blind hole 20 of the swing cylinder 21.

According to the invention is further in this context that in the region of the working piston 24 rotatably on the pump shaft 4, an eccentric bushing 27 is arranged in the pump shaft side a circumferentially surrounding the impeller 5 adjacent arranged Ansaugringkanal 28 is arranged.

It is also essential to the invention that a crank disk ring 29 with a piston bore 30 for the working piston 24 is rotatably arranged on the outer jacket of the eccentric bushing 27, wherein a suction kidney 31 is arranged in the region of the piston bore 30 in the eccentric bushing 27 in such a way that when the eccentric bushing revolves with the pump shaft 4 27 located in Ansaugringkanal 28 medium is conveyed into the piston passage bore 25. It is also advantageous if 24 piston rings 44 are arranged on the outer circumference of the slidably mounted in the piston bore 30 of the crank disk ring 29 region of the working piston, which at low Production and assembly costs ensure a high efficiency of the arrangement according to the invention.

Another feature of the invention is that the impeller 5 bears against both the eccentric bushing 27 and the crank disk ring 29 and has at least one, the Ansaugringkanal 28 adjacent arranged collecting ring channel 33, wherein the contact region of the impeller 5 on the eccentric bushing 27 as an annular gap filter 32 is formed, so that in this area a transfer of medium from the pump interior 14 into the collecting ring channel 33 / the collecting ring channels 33 and of this / these in the Ansaugringkanal 28 is possible.

It is essential that, as in the FIG. 5 shown, the annular gap filter 32 at the same time fulfills the function of a centrifugal separator and consists of a arranged on the eccentric bush 27 annular Filterplato 45, are introduced in the Filterkeilnuten 46 that from the outer radius of the gap filter 32 located filter inlet 47 to the inner radius of the gap filter 32, so that particles entrained by the coolant (such as chips or grains of sand) can not penetrate into the area of the gap filter 32, and even with the smallest particles sucked in, a good flow through the filter results in the interior strongly widening Filterkeilnuten 46 is ensured, with particles adhering to the filter at the same time are discharged in the filter particles acting as a result of the forces acting on these centrifugal forces.

In another in the FIG. 7 illustrated embodiment of the annular gap filter 32 is formed by a filter disc 49, wherein in the region of the filter disc in the eccentric bushing 27, a plane of the eccentric bushing 27 superior, projecting into the pump interior 14 scraper 50 is arranged obliquely to the tangent to the filter disk 49, that in the region of the slit filter 32 "entrained" particles (such as, for example, chips or grains of sand) are discharged towards the pump interior 14 when the impeller 5 rotates.

Characteristic is also that between the bore outlet of the blind hole 20 and the pressure channel 13, a check valve 34, and in front of the solenoid valve 12 between the pressure channel 13 and the pressure chamber 16 a passage bore 35 is arranged, wherein the solenoid valve 12 causes a defined pressurization of the control slide 7 ,

Will now be in this invention, in the FIG. 1 shown arrangement on the pump shaft 4 rotatably mounted impeller 5 is driven, so at the same time the non-rotatably mounted on the pump shaft 4, provided with the Ansaugringkanal 28 and the Ansaugniere 31 eccentric bushing 27 is set in a rotary motion. At the same time the rotatably arranged on the outer surface of the eccentric bushing 27 crank disk ring 29 is offset with its piston bore 30 in strokes.

The arranged in the piston bore 30 working piston 24 with its piston passage bore 25 easily oscillates in circumferential eccentric bushing 27 to the provided with the blind hole 20 swivel cylinder 21, in the blind bore 20 via the passage bore 26, the piston passage bore 25 opens.

That in the FIG. 1 Vane 5 shown in section abuts both the eccentric bush 27 and the crank disk ring 29 and has an outer collecting ring channel 33 adjacent to the split filter 32 and an inner collecting ring channel 33 adjacent to the intake ring channel 28.

Both collecting ring channels 33 are interconnected by means of overflow holes 43.

In the region of the annular gap filter 32, as in the Figures 5 and 7 shown, may be formed, a passage of cooling medium from the pump interior 14 behind the impeller 5 in the outer collecting ring channel 33 and over the overflow holes 43 in the inner collecting ring channel 33 and of this / these in the Ansaugringkanal 28 is ensured.

The arrangement according to the invention with the intake kidney 31 arranged in the eccentric bush 27, the intake ring channel 28, now effects at, as in the Figures 2 and 3 a defined "conveying" of the cooling medium from the Ansaugringkanal 28 via the Ansaugniere 31 in the piston bore 30 and from there via the Kolbendurchlochbohrung 25 and the passage bore 26 into the blind hole 20 of the pivot cylinder 21.

The stroke of the working piston 24 in the piston bore 30 of the crank disk ring 29 in the present embodiment game per revolution about 1 mm to 2 mm because due to the inventive arrangement already very low flow rates for accurate actuation / displacement of the control slide 7 sufficient.

The actuation of the control slide is now carried out by the conveyed into the blind hole 20 cooling medium via the (a backflow preventing) check valve 34 is pressed into the pressure channel 13.

This pressure channel 13 opens on the one hand via the passage bore 35 into the pressure chamber 16 formed by the spring plate 17 and the pump housing 1 with the pressure-dependently slidably mounted in the pressure chamber 16 control slide 7, and on the other hand in the solenoid valve 12, wherein the solenoid valve 12 outlet openings are arranged in a arranged in the pump housing 1 Rückstömkanal 15 open, which is directly connected to the pump interior 14.

According to the invention, the solenoid valve 12 is normally open.

In the case of an "open" solenoid valve 12, the arrangement according to the invention conveys cooling medium "without pressure" via the outlet openings 36 of the solenoid valve 12 into a ring channel 37 arranged in the working housing 11, which opens into a return flow channel 15, via which the cooling medium flows back into the pump interior 1.

If necessary, the pressure in the pressure channel 13 by means of the solenoid valve 12 is increased continuously.

The subsidized by the inventive arrangement cooling medium is pressed into the pressure chamber 16.

There, the thus injected cooling medium causes a defined (via the solenoid valve 12) adjustable pressurization of spring-loaded by the return spring 6 control slide. 7

The return spring 6 is located on the side facing away from the impeller 5 of the outer cylinder 8 of the control slide 7, to the spring systems 38 at.

It is advantageous in this context, if in the outer surface of the pressure chamber 16 in the pump housing 1, one / more guide / e 39 is arranged / are, the / ensures optimal, low-friction and precise guidance of the control slide / ensure.

In this context, it is also advantageous that an outer scraper 40 and the slider inner seal 18 adjacent to the pump inner space 14 in the spring plate 17 are arranged in the pump housing 1 adjacent to an inner scraper 41 which prevents the entry of particles entrained by the coolant (such as, for example, FIG Chips, grains of sand, etc.) in the working area of the adjacent slide seals, thereby not only increasing the reliability and the life, but also significantly reducing the frictional losses and thereby the operating accuracy, ie improve the fine adjustability.

This defined pressurization, the cross-sectional area of the control slide 7, now allows an exact translational displacement of the control slide 7 and thus a precisely adjustable overlap of the outflow of the impeller 5 through the outer cylinder 8 of the control slide. 7

Due to the arrangement according to the invention, an exact control of the delivered coolant volume flow is realized via the so effected, defined displacement of the control slide 7.

After the heating phase of the motor (with the closed control slide 7), the pressure in the pressure passage 13 can be precisely controlled by means of the solenoid valve 12 and thus a defined method of the control slide 7 along the outer edge of the impeller 5 realized, which in turn affects the engine temperature very accurately in continuous operation can be, so that Both the pollutant emissions as well as the friction losses and fuel consumption can be significantly reduced in the entire working range of the engine.

Even with unfavorable thermal boundary conditions, e.g. in the vicinity of the turbocharger and very limited installation space for the coolant pump in the engine compartment, the solution according to the invention ensures optimum cooling with minimal construction volume due to the arrangement of an integrated in the pump housing 1 and at the same time cooled by the coolant in the pump housing 1 solenoid valve 12.

In addition, the solution according to the invention enables a reliable actuation of the control slide 7 with a very low drive power.

Even in case of failure of the scheme according to the invention, a further functioning of the coolant pump (fail-safe) is ensured because in the de-energized state, the solenoid valve 12 is open, so that the pressure in the pressure channel 13 and in the pressure chamber 16 drops, so that the return spring. 6 the control slide 7 moves in this case in the (rear) working position "OPEN".

When spring-loaded "retraction" of the control slide 7 in the "fail-safe position", the pumped from the inventive arrangement cooling medium from the pressure channel 13 via the open solenoid valve 12 in the return flow 15 and from there into the pump interior 14 of the coolant pump of the invention.

Due to the inventive Zwanglaufes by the eccentric drive of the pump according to the invention, the present solution is suitable even for high speed applications.

The solution according to the invention is characterized in particular by their very short in their length design, which can take advantage of very small space available in the engine compartment space optimally.

The coolant pump according to the invention is manufacturing and assembly technology very easy and inexpensive to produce, is also in connection with the construction of different pump series and Sizes "standardizable" and requires no factory air-free filling.

In addition, the controllable coolant pump according to the invention can be easily and inexpensively integrated into the engine management. It ensures high volumetric efficiency, a very high reliability with very high reliability.

REFERENCE SYMBOL

1

pump housing

2

pump bearings

3

pulley

4

pump shaft

5

impeller

6

Return spring

7

regulating slide

8th

outer cylinder

9

seal Housing

10

Shaft seal

11

labor housing

12

magnetic valve

13

pressure channel

14

Pump interior

15

backflow

16

pressure chamber

17

spring plate

18

Slide inner seal

19

Slider outer seal

20

Blind hole

21

swing cylinders

22

bore end

23

Piston contact bar

24

working piston

25

Kolb passage bore

26

Through bore

27

eccentric

28

Ansaugringkanal

29

Crank ring

30

piston bore

31

Ansaugniere

32

edge filter

33

Collecting ring channel

34

check valve

35

Through bore

36

outlet

37

annular channel

38

suspension system

39

guide element

40

Outer scraper

41

Internal scraper

42

Flügelradbuchse

43

overflow holes

44

piston rings

45

filter Plato

46

Filterkeilnut

47

filter inlet

48

filter outlet

49

filter disc

50

scraper

Claims (9)

1. Controllable coolant pump with a pump housing (1), a pump shaft (4) in a pump bearing (2) powered by a belt driven pulley (3) in / at the pump housing (1), an impeller (5) located in a torque-proof manner at a free end on the flow side of this pump shaft (4), a pressure operated gate valve (7) spring loaded with a return spring (6) with a variably covering exterior cylinder (8) at the discharge area of the impeller (5) an annular shaft seal (10) arranged in a sealing gland (9) in the pump housing (1) between the impeller (5) and the pump bearing (2), with a working housing (11) arranged at the pump housing (1) where a solenoid valve (12) is arranged with a pressure duct (13) leading to its inlet port and a return flow port (15) opening out into the pump interior compartment (14) leading to its flow outlet port, whereby a spring plate (17) forms a pressure chamber (16) with the pump housing (1) in the pump interior compartment (14) at the pump housing (1) where the return spring (6) fits, characterized by the fact

   - that an inside gate valve seal (18) is located on the external radius of the spring plate (17) in such a way that this fits at the exterior cylinder (8) of the gate valve (7), whereby an outside gate valve seal (19) is also arranged externally on the exterior cylinder (8) of the gate valve (7) in the pump housing (1) so that the exterior cylinder (8) of the gate valve (7) can be moved variably along the discharge area of the impeller (5) against the force of the return spring (6) when pressure is built up in the pressure chamber (16), and

   - that a swivel cylinder (21) is arranged in the pump interior compartment (14) between the impeller (5) and the equipment area of the spring plate (17) at the pump housing (1) so that it is torque-proof in the pump housing (1) and projects through the spring plate (17), with a blind hole (20) closed towards the pump interior compartment (14) whose exit hole (22) opens out into the pressure duct (13) and where a piston mechanism bar (23) is located at its opposite end, whereby a rotatable working piston (24) with a piston passage hole (25) is arranged on the swivel cylinder (21), whereby the piston passage hole (25) opens out above an open passage hole (26) arranged in the swivel cylinder (21) in the area of the piston passage hole (25) in the blind hole (20) of the swivel cylinder (21), and

   - that an eccentric bush (27) is arranged in a torque-proof manner on the pump shaft (4) in the are of the working piston (24) where an adjacent annular intake duct (28) is arranged to surround the entire circumference of the impeller (5), and

   - that a rotatable crank disk ring (29) with a piston hole (30) for the working piston (24) is arranged on the outside casing of the eccentric bush (27), whereby an intake manifold (31) is arranged in the eccentric bush (27) in the area of the piston hole (30) in such a way that medium located in the annular intake duct (28) for the eccentric bush (27) rotating with the pump shaft (4) is moved to the piston passage hole (25), and

   - that the impeller (5) fits at the eccentric bush (27) and also at the crank disk ring (29) and has at least one collecting ring duct (33) adjacent to the annular intake duct (28) whereby the plant area of the impeller (5) at the eccentric bush (27) is constructed at the eccentric bush (27) as an annular gap filter (32) enabling the medium to pass in this area from the pump interior compartment (14) into the collecting ring duct(s) (33) and from this / them into the annular intake duct (28), and

   - that a non-return valve (34) between the bore outlet of the blind hole (20) and the pressure duct (13) and an open passage hole (35) is arranged in front of the solenoid valve (12) between the pressure duct (13) and the pressure chamber (16) where the solenoid valve (12) exerts a defined pressurisation of the gate valve (7).
2. Controllable coolant pump according to claim 1 characterized by the fact that one / several spring unit(s) (38) is / are arranged on the side of the exterior cylinder (8) of the gate valve (7) facing away from the impeller (5).
3. Controllable coolant pump according to claim 1 or claim 2 characterized by the fact that one / several guide element(s) (39) is / are arranged in the casing surface of the pressure chamber (16) in the pump housing (1).
4. Controllable coolant pump according to claim 1 to 3 characterized by the fact that an outer wiper (40) is adjacent to the outside gate valve seal (19) in the pump housing (1) and / or an inner wiper (41) in the spring plate (17) is adjacent to the inside gate valve seal (18) in the direction of the pump interior compartment (14).
5. Controllable coolant pump according to claim 1 to 4 characterized by the fact that an impeller bush (42) is arranged in the impeller (5).
6. Controllable coolant pump according to claim 1 to 5 characterized by the fact that when there is an arrangement of several collecting ring ducts (33) in the impeller (5) and / or in the impeller bush (42), these are connected between each other and with each other by using overflow holes (43).
7. Controllable coolant pump according to claim 1 to 6 characterized by the fact that piston rings (44) are arranged on the outer circumference of the moveable mounted area of the crank disk ring (29) working piston (24) in the piston hole (30).
8. Controllable coolant pump according to claim 1 to 7 characterized by the fact that the annular gap filter (32) functions simultaneously as an annular filter plateau (45), arranged on the eccentric bush (27), where the filter keyways (46) are arranged in such a way that they enlarge from the filter entry (47) on the outside radius of the gap filter (32) towards the filter exit (48) located on the interior radius of the gap filter (32).
9. Controllable coolant pump according to claim 1 to 8 characterized by the fact that the annular gap filter (32) is formed by a filter disk (49) whereby one or several wipers (50) in the eccentric bush (27) in the zone of the filter disk (49) with them penetrating into the pump interior compartment (14) projecting from the plane of the eccentric bush (27) and being placed tangentially to the filter disk (49) so that the particles carried by the rotating impeller (5) in the filter gap are transported to the pump interior compartment (14).

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