US 3252422 A
Description (OCR text may contain errors)
May 24, 1966 J. L. STULENS CIRCULATING TURBOPUMP, PARTICULARLY FOR CENTRAL HEATING PLANTS 4 Sheets-Sheet 1 Filed May 13, 1964 in i NN m y 1966 i J. L. STULENS 3,252,422
CIRCULATING TURBOPUMP, PARTICULARLY FOR CENTRAL HEATING PLANTS Filed May 15, 1964 4 Sheets-Sheet 2 May 24, 1966 J. STULENS 4 Sheets-Sheet 5 Filed May 13, 1964 May 24, 1966 J. 1.. STULENS CIRCULATING TURBOPUMP, PARTICULARLY FOR CENTRAL HEATING PLANTS 4 Sheets-Sheet 4 Filed May 15, 1964 7 3,252,422 QllRCULATlNG TURBOPUMP, PARTICULARLY FOR CENTRAL HEATING PLANTS .lean Louis Stulens, 23 Rue du Tulipier,
. Brussels, Belgium Filed May 13, 1964, Ser. No. 367,166 Claims priority, application Belgium, May 15. 1963, 506,393, Patent 632,364; Jan. 30, 1963, 516,033, Patent 643,173
18 Claims. (Cl. 103-97) My invention relates to circulating pumps (turbopumps), particularly for central heating installations.
It is known in central heating installations to use a circulating pump but that there is a difiicu-lty as regards the determination of the direction of movement of the rotor.
A means frequently used is to provide an inspection window arranged so as to be able to check the direction of rotation of the motor from the outside.
An arrow showing the direction of movement and a checking inspection through the window do not however give complete security because experience has shown that the arrow fixed or painted on the machine may give rise to errors.
Furthermore, the inspection window is often soiled by impurities in the water, particularly limestone and rust.
On the other hand, there are types of pumps with automatic priming which permit rotation in either direction, but when the direction of rotation is reversed, the direction of flow is likewise reversed, that is to say the suction side becomes the delivery side.
Now the fact must not be overlooked that any element for providing a circulation (e.g. pump, agitator) can be driven by a single-phase electric motor or by an internal combustion engine, which implies in this case one direction of circulation only and requires a special turbine for each case, because of the great difliculty in adapting internal combustion engines to direct coupling.
Whenever a circulation-providing member is placed in a pump-connecting system or installation, it is impossible to avoid checking the direction of rotation. If the direction of rotation of the turbine should be reversed and if the electric current is three-phased, it is sufficient to reverse two phases, but for the single-phase or internal combustion engine the turbine has to be replaced in order to avoid danger of the flow being opposed to that of the thermosiphon. For instance, in the case of heating the circulation may be stopped or a considerable braking effect may occur and may lead to an overheating of the water in the boiler.
An object of this invention is to overcome these ditficulties and in particular to avoid the use of an inspection window.
The invention is also directed to obviating certain disadvantages and certain difficulties connected with the present system involving a by-pass, which become neces sary because if this latter is omitted the circulation may be stopped.
Known by-pass devices comprise a tapping which is completely separate and independent; such an arrangement is expensive, necessitates at least three valves and gives rise to difficulties because frequently the space required is not available.
Gear pumps are also known and self-priming pumps provided with a separate 'by-pass connected to a safety valve or a pipe for discharging overpressures are known, but these systems are very different in design from that which is the basis of the invention.
In short, the impurities in the water cause a blockage United States Patent 3,252,422 Patented May 24, 1966 of the rotor of the motor which makes it necessary to dismount the fittings.
If there is no bypass the installation has to be stopped and emptied and if there is a by-pass exteriorly to the appliance the cost is considerably increased and more space is required;
According to the invention there is provided in the frame-work of the pump a passage forming a by-pass (incorporated .by-pass) between the fluid entry side and the turbine outlet side and also a system of valves in which a double-acting valve actuated from outside the framework of the pump can occupy two positions: one in which it is in contact with a seating situated at the entry to the turbine and the other in which it is in contact with a seating provided at the entry of a by-pass, while a second valve also actuated from outside the framework co-operates with a seating provided at the outlet or delivery side of the turbine.
The invention will next be described in conjunction with the attached drawings, wherein:
FIGURES 1 and 2 are views in vertical section showing the framework of the pump and also the turbine and the motor, the valve systems being in two different positions;
FIGURES 3 and 4 are sections along lines IIIIII and IVIV in FIG. 1; and
FIGURES 5 to 10 are diagrammatic views of variants of the form of the blades.
In FIGURE 1 is shown a turbine consisting of two flanges 1 and 2 with one of which the inlet body 3 of the turbine is integral, which rotates in a sleeve 4 (FIG- UR E 1) forming part of the framework 5 of the pump,
while the other flange 2 carries the socket 6 which is keyed on the shaft 7 of the motor 8 fixed to the framework by bolts 9.
In accordance with the invention the blades P are of a special form in that they comprise (FIGURES 7 and 8) two profiles which are symmetrical in relation to the 1ongitudinal axis of the blade, in such a way that the turbine is double-acting, that is to say that whatever the direction of rotation the direction of flow of the liquid remains unchanged.
In such a machine no inspection window is necessary because it delivers equally well in either direction while preserving the same direction of flow of the fluid.
Such a feature is therefore applicable to any machine used for moving a fluid.
As shown in FIGURES 1 and 2, in the framework 5 of the pump there is provided between the fluid entry side and the outlet side a passage 10 forming a by-pass, and a valve 11 is provided which is actuated by a rod 12 provided with a control wheel 13 and which can occupy two positions; one in which the valve is in contact with the seating formed by the sleeve 4 at the entry of the turbine and the other in which it is in contact with a seating or sleeve 14 provided at the entry of the incorporated by-pass '10.
A second valve 15 actuated by a rod 516 provided with a control wheel :17 co-operates with a seating d8 provided at the outlet '19 or discharge point of the turbine.
When the doubleaacting valve 11 is in the position shown in FIGURE 4, that is to say is in contact with the seating 14, and if the valve 15 has been opened, circulation takes place forced by the turbine, as shown by the arrows in FIGS. 1, 3 and 4.
When these valves are in the position shown in FIG- URE 2, with the valve 15 closed and the valve 1 1 in contact with the seating 4 (that is to say closure of the suction side of the turbine) the passage 10 acts as a by-pass permitting free and direct flow, which makes it possible to dismount the motor and the turbine without other precautions having to be taken while the installation continues to act as a thermosiphon.
By opening the valves, the thermosiphon circulation ceases automatically, and forced circulation through the turbine is re-established.
An arrangement such as that shown in FIGURES 1 and 2, making possible a straight-line circulation in the pipeline, gives rise to an assembly which permits a considerable saving in labor and material.
These advantages may be summarized as follows:
( 1) Less space required.
(2) Simpler construction, fewer tappings, less welding and less risk.
(3) Very simple and easy mounting.
(4) In case of repair the motor and turbine can be dismounted without any other precaution than that of closing the valves.
(5) The dirt trap chamber can be rinsed out without dismounting.
(6) By arranging the handwheels'13 and 17 as shown and by giving them suitable dimensions the risk of error in operation is avoided, because before applying the valve 15 on its seating 18, that is to say obstructing the turbine outlet 19, it is necessary to apply the valve 11 on its seating 4; there is no risk therefore of closing the by-pass 10 and at the same time obstructing the turbine outlet, which would stop the circulation of water in the piping, could cause this water to boil and could therefore seriously damage the plant. Vice versa, before applying the valve 11 on the seating 14 and therefore obstructing the by-pass 10, it is necessary to open the valve 15, which avoids the drawback mentioned above. It would therefore be impossible to apply the valve 11 on the seating 14 without first of all opening the valve 15, removing it from the seating 18. On the other hand if in error the valve 11 is brought on the seating 4, while it has been forgotten to move the valve 15 to bring it into contact with the seating 18, the by-pass would function normally and in the case of dismounting of the motor and of the turbine, the oversight would be quickly noticed because water would then flow through the by-pass at the level of the turbine discharge point and at this moment it would become necessary to close the valve 15, to bring it on to its seating 18.
According to the invention, means are provided such that the liquid can be discharged as freely as possible, and to obtain a better balance of the turbine and also a better distribution of wear of the bearing, and for this purpose there is mounted on the motor shaft a balance component which is locked between the motor and the pump framework and which comprises a peripheral recess extending to a position near the turbine socket and communicating with the outlet and in the framework of the pump is provided a circular cavity arranged in such a way as to provide a communication between the spaces between the blades and the recess in the balance component.
For this purpose on the socket 6 carried by the shaft 7 of the motor is mounted a balance component which is positioned between the motor 8 and the framework 5 of the pump. The component 20 has a peripheral recess 21 extending to a position near the socket 6 of the turbine and communicating with the outlet 19.
On the other hand, in the framework 5 of the pump is provided a circular cavity 22 which is arranged so as to provide a communication between the spaces 23 between the blades P and the recess 21 in the component 20. The result is that the liquid which might tend to accumulate in the spaces 23 between the flanges 1 and 2 and the blades P, finds a discharge outlet through the cavity 22, the recess 21 and the discharge point.
It will be understood that this discharge can thus be effected more freely and that the turbine is thus better balanced,
This component 20 is provided on the motor side with a slot 25 which is connected through holes 26 with the recess 21 in such a way as to permit the circulating fluid to lubricate and cool the motor 8 with suflicient pressure.
In the slot 25 is provided a filter 27, of felt, for example, to prevent the passage of solid particles.
As will be understood, it is possible to obtain two different rates of flow as requisite and according to the direction in which the turbine is rotating.
It will then be suflicient to calculate and to design the profile of the bladings in an asymmetrical manner corresponding to each of the two rates of flow.
The thickness of the blade can for instance be greater on the side of the entry flange 1 than on the side of the rear flange 2.
This difference is shown in FIGURES 6 and 8 at a selected point by e and e The edges 25 of the blades (FIGURE 6) are therefore inclined at an angle a, for instance 15 to the perpendicular connecting the flanges.
As shown in FIGURE 9, the number of blades may be more than three and may be any number, for instance five.
On the other hand, the blade may be asymmetrical in relation to a radius (FIGURE 10) in order to have a given rate of flow for one direction of rotation and another rate of flow for the other direction of rotation.
There can be provided through the rod 12 of the valve 11 a bore 28 (FIGURES 1 and 2) which permits the insertion of a screwdriver which can engage in a slot 29 in the shaft 7 of the motor which enables the motor to be set in operation when first starting.
When the valves 11 and 15 are in the position in FIG- URE 2, if the operator only unscrews the fixing nut 30 of the control handwheel 13 of the valve 11 to introduce a screwdriver through the bore 28 and to reach the slot 29, the rotor can be unkeyed at any moment of operation of the installation without any serious danger of obstructing the circulation, because by closing the valves the forced circulation is cut and the by-pass is automatically opened with direct passage and only a few drops of water will emerge at the moment when the nut 30 is removed. As soon as the rotor is unkeyed and the motor therefore in operation, the two valves are brought back into the forced circulation position, but only after putting the nut 30 back into place.
As an additional advantage, it is thus possible to obtain any desired setting of the rate of flow, because by bringing the valve 11 into a position slightly displaced from the seating 14 a very sensitive regulation of the rate of flow is obtained.
What I claim is:
1. A circulating pump comprising a framework and a turbine supported for rotation in the latter, said framework having an inlet for passage of fluid to the turbine and an outlet for passage of fluid from the turbine, said framework further having a by-pass passage between the fluid inlet and the outlet, externally operable doubleacting valve means supported in said framework and operable between two positions in one of which the by-pass passage is opened and the turbine inlet is closed and in the other of which positions the by-pass passage is closed and the turbine inlet is opened, and externally operable second valve means supported in said framework for selectively opening and closing said outlet, said valve means by virtue of their support in the framework being effective to directly act on the inlet and outlet of the turbine as well as on the by-pass passage.
2. A circulating pump according to claim 1 comprising a motor supported on said framework and driving said turbine, the pump further comprising a balance component which is locked between the motor and the framework and provided with a peripheral recess communicating with the outlet of the turbine, said framework being provided with a circular cavity providing communication between the turbine inlet and the recess of the balance component.
3. A circulating pump according to claim 2 wherein the balance component is provided on the motor side with a slot connected by holes with theperipheral recess of the turbine to permit the circulating fluid to lubricate and cool the motor with sufficient pressure.
4. A circulating pump according to claim 3 comprising a filter in said slot in the balance component.
5. A circulating pump according to claim 1 wherein said turbine has blades with two profiles which are symmetrical in relation to the longitudinal axis of the blade such that whatever the direction of rotation of the pump, the direction of flow of the liquid is the same.
6. A circulating pump as claimed in claim 5 wherein said blades have an asymmetrical shape to obtain two different rates of fluid flow for the different directions of pump rotation.
'7. A circulating pump according to claim 5 wherein said turbine has an entry flange and a rear flange, the thickness of the blade being greater on the side of the entry flange than on the side of the rear flange.
8. A circulating pump according to claim 7 in which the edges of the blades are inclined at an angle of about 15 between the flanges.
9. A circulating pump according to claim 1 wherein said first valve means has a rod in which is provided a bore which permits the insertion of a screwdriver which can engage a slot in a shaft of a motor which drives the turbine to permit the setting in operation of the motor when first starting.
10. A circulating pump comprising a framework and a turbine supported for rotation in the latter, said framework having an inlet for passage of fluid to the turbine and an outlet for passage of fluid from the turbine, said framework further having a by-pass passage between the fluid inlet and the outlet, said by-pass passage having an inlet which is opposed to the turbine inlet, a valve supported in said framework and operable externally thereof for movement between a first position in which the inlet to the by-pass passage is closed and the turbine inlet is open and a second position in which the turbine inlet is closed and the inlet to the by-pass passage is open, and a second valve which is supported in said framework and is operable externally thereof for selectively closing the turbine outlet.
11. A circulating pump as claimed in claim 10 wherein said valves are operatively associated with one another such that said turbine outlet can be closed by the second valve only after the first valve has closed the turbine inlet and opened the inlet to the by-pass passage, whereas said turbine inlet can be opened only after the turbine outlet has been opened by said second valve.
12. A circulating pump as claimed in claim 11 comprising control rods for said valves and wheels on said rods, said rodshaving different lengths whereby said wheels are associated with one another such that said turbine outlet can be closed by the second valve only after the first valve has closed the turbine inlet and opened the inlet to the by-pass passage, whereas said turbine inlet can be opened only after the turbine outlet has been opened by said second valve.
13. In a motor and impeller assembly in a liquid circulating system: a framework having a liquid inlet and a liquid outlet, the impeller comprising two spaced flanges one of which includes an integral inlet body portion, a sleeve in said framework and in which said inlet body portion is rotatably supported, means for securing the motor to the framework, a socket keyed to the motor for rotation therewith and carried by the second of said flanges, said framework defining a passage forming a bypass between the liquid inlet and the liquid outlet, said by-pass having an inlet and an outlet, a first seating disposed at the inlet body portion of the impeller, a second seating disposed at the inlet of the by-pass, a double acting valve actuated from outside the framework and adapted to occupy two positions, one in which it is in contact with the seating at the inlet of the by-pass and the other in which it is in contact with the seating at the inlet body portion of the impeller, said impeller having a liquid outlet, a third seating at the outlet of the impeller, a second valve also actuated from outside the framework and adapted to contact said third seating such that when said first valve is in contact with said second seating and the second valve has been opened, circulation takes place through said impeller, whereas when the second valve is in contact wtih the third seating and the first valve is in contact with the first seating the by-pass passage permits free and direct liquid flow therethrough which enables dismounting of the motor and of the impeller while the circulation continues to act as a thermosiphon.
14. In an assembly according to claim 13, in which a balance component is disposed between the motor and the framework and is coupled to the motorin driving relation, said motor including a drive shaft, said impeller including a hub mounted on said drive shaft coupled to said second flange, and spaced blades between and secured to said flanges, said balance component having a peripheral recess extending proximate the hub of the impeller and communicatingwith the impeller outlet, said framework being provided with a circular cavity which is arranged to provide permanent communication between the spaces between the impeller blades and the recess in the balance component.
15. In an assembly according to claim 14, in which the balance component is provided with a slot facing the motor and has holes extending between said slot and said peripheral recess whereby the circulating fluid is adapted to cool and to lubricate the motor.
16. In an assembly as claimed in claim 13 wherein a filter is disposed in said slot in the balance component for filtering the circulating fluid used for cooling said motor.
17. In an assembly according to claim 13, in which the blades have a thickness which is greater in a region adjacent said one flange compared to that adjacent the other flange.
18. In an assembly according to claim 13, in which the blade is asymmetrical in relation to a radius of the impeller so as to have a given rate of flow for one direction of rotation and another rate of flow for the opposite direction of rotation.
7 References Cited by the Examiner UNITED STATES PATENTS 983,137 1/1911 Heald 103-103 1,105,808 8/1914 Macneill 103112 1,829,122 10/1931 Wade 103103 2,235,706 3/1941 Hanus 230114 2,779,290 1/1957 Wiegers 10339 3,135,211 6/1964 Pezzillo 10387 FOREIGN PATENTS 57,124 6/ 1891 Germany.
ROBERT M. WALKER, Primary Examiner.