Patent Application
20220154625
The present application claims priority under 35 U.S.C. § 119 to German Application No. 10 2020 130 553.2, filed on Nov. 19, 2020, the entire contents of which are hereby incorporated herein by reference.
The present disclosure relates to a pump device of a cooling circuit of an internal combustion engine of a commercial or motor vehicle, to a commercial or motor vehicle, and to a method for operating such a pump device.
In the commercial vehicle (CV) sector, controllable mechanical main water pumps or combinations of mechanical main water pumps with electrical auxiliary pumps are conventionally used for cooling combustion engines. The main water pumps are designed for maximum engine load at high engine speeds and are therefore often oversized in operating conditions with low engine speeds. Their flow rate is exclusively linked to the engine speed—and not to the actual cooling demand corresponding to the operating condition of the engine. The motor of the pump must therefore apply a mechanical power of up to two kilowatts for its function in the cooling circuit. In addition, the controllability of mechanical pumps is limited. The fuel-saving potential that could be achieved through flow rate control is therefore not fully exploited.
Example embodiments of the present disclosure provide pump devices to each supply coolant to an internal combustion engine of a commercial or motor vehicle, with improved efficiency.
Example embodiments of the present disclosure provide a pump device of a cooling circuit of an internal combustion engine of a commercial or motor vehicle, a commercial or motor vehicle, and a method of operating such a pump device.
A pump device according to an example embodiment of the present disclosure provided to a cooling circuit of an internal combustion engine of a commercial or motor vehicle includes two electric pumps in parallel, each of which includes a switchable backflow valve in a suction line, so that the electric pumps can optionally be operated individually or in parallel. Trucks mainly drive in the partial load range. The volume flow required can be provided in a single operation. The efficiency of the pump device can thus be increased considerably, because the pump efficiency when operating a small pump close to a design point is higher than a pump efficiency of a larger pump in a partial load range.
Preferably, the switchable backflow valves are 2/2-way valves, which can be actuated pneumatically or electrically.
Preferably, the switchable backflow valves prevent a backflow of a coolant in the cooling circuit when in a blocking position, so that the electric pumps cannot cause coolant to flow through in a direction opposite to the conveying direction.
One of the electric pumps may define a main pump which is operated in a normal condition and whose associated switchable backflow valve is in the flow position, the second of the electric pumps defining a secondary pump which is switched off in the normal condition and whose associated switchable backflow valve is in the shut-off position. The pumping device is then operated in a single mode. It may be advantageous if, in a single operation, the pumps alternate so that the running time can be distributed equally between the two pumps.
Preferably the electric pumps are identical. Costs for the construction of a larger pump can thus be saved. By having a larger number of identical pumps, manufacturing costs can also be kept low. The presence of two identical pumps also creates redundancy in case of failure of one of the pumps.
Preferably, the pump device includes an adapter housing in which the switchable backflow valves are located, the electric pumps being attachable to the adapter housing and the adapter housing including an interface to an internal combustion engine. The pump device can thus be connected to already existing interfaces and can be easily retrofitted.
Preferably, the adapter housing includes a flange side to connect to a cooling circuit of an internal combustion engine, to which an suction flange including a third sealing surface and a discharge flange including a fourth sealing surface are provided. The adapter housing further includes a pump side opposite the flange side to connect to the electric pumps. The adapter housing further includes a first discharge line and a second discharge line, the suction lines, and a first pump working space adjoining a first of the suction lines and surrounded by a first sealing surface, and a second pump working space adjoining a second of the suction lines and surrounded by a second sealing surface, and a valve assembly including the two switchable backflow valves, which are adjustable between a blocking position and an open position. At least one of the pump working chambers defines an opening in the pump side, preferably each pump working chamber defines an opening in the pump side, and the discharge flange is connected to the two discharge lines via a discharge connection piece, and the suction flange is connected to the two suction lines via a suction connection. In each case a switchable backflow valve cooperates with one of the two suction lines and closes the corresponding suction line in the closed position and releases the corresponding suction line in the open position.
The switchable backflow valves can preferably be operated from the outside.
It is advantageous if the suction connection downstream of the suction flange opening is divided into the two suction lines.
Preferably, the discharge lines join to define the discharge port located upstream of the discharge flange opening.
Preferably, the suction manifold has a larger cross-section than one of the suction lines.
In addition, it is advantageous if the discharge port has a larger cross-section than one of the discharge lines.
In an advantageous example embodiment, a first one of the two switchable backflow valves is located in a transition region between the first suction line and the first pump working chamber, and a second one of the two switchable backflow valves is located in a transition region between the second suction line and the second pump working chamber.
Furthermore, a commercial or motor vehicle is provided with an internal combustion engine which can be cooled by a cooling circuit, and with a pump device described above which is adapted to circulate a coolant in the cooling circuit. The pump device is preferably connected to the corresponding internal combustion engine via the suction flange and the discharge flange.
An example embodiment of a method of operating a previously described pump apparatus includes the steps of, in the event that the required flow rate in the cooling circuit is low, at or below a predetermined threshold value, operating the pumping device in a single mode, with the backflow valve of the operated electric pump in a flow position and the backflow valve of the switched-off electric pump in a shut-off position; and in the event that the required flow rate in the cooling circuit is high, at or above a predetermined threshold value, operating the pumping device in a parallel mode, with both electric pumps operating and the backflow valves in the flow position.
Preferably, the method includes the following additional steps of, in the event of failure of one of the electric pumps, operating the other electric pump, and setting the associated backflow valve to the flow position, and setting the backflow valve of the faulty pump to the shut-off position.
The pump device is preferably a portion of a commercial or motor vehicle with an internal combustion engine, the internal combustion engine being cooled by a cooling circuit with the pump device circulating coolant in the cooling circuit.
The above and other elements, features, steps, characteristics and advantages of the present disclosure will become more apparent from the following detailed description of the example embodiments with reference to the attached drawings.
In the following, example embodiments of the present disclosure are described with reference to the drawings. Identical components or components with identical functions bear identical reference signs.
The pump device 1 preferably includes two identical electric pumps 2,3 connected in parallel. In the respective suction line 4 of the two pumps 2,3, a backflow flow valve 5,6 is provided in each case. The backflow valves 5,6 are switchable. One of the electric pumps 2 defines the main pump. The other electric pump 3 serves as a slave pump. The first backflow flow valve 5 arranged upstream of the main pump 2 is spring-biased and pneumatically operable. When the main pump 2 is operated, the backflow flow valve 5 can be flowed through in a flow position in the delivery direction. When the main pump 2 is switched off, the first backflow flow valve 5 is actuated and transferred into a blocking position against the spring force. The second backflow valve 6, which is arranged upstream of the secondary pump 3 in the direction of flow, can be actuated electrically by means of an electromagnet which has two windings acting in opposite directions. In the event that the secondary pump 3 is not operated, the second backflow valve 6 is in a blocking position. If, on the other hand, the secondary pump 3 is used, the second backflow valve 6 is transferred to a flow position.
Commercial vehicles, especially trucks, mainly drive in the partial load range, the required volume flow can then be generated by a single one of the two electric pumps 2,3. The backflow valves 5,6 in the suction area of the electric pumps 2,3 prevent an undesired backflow of the coolant through the passive electric pump in single operation. The pump efficiency is increased, as this is greater with a smaller pump being operated close to the design point than the pump efficiency of a large pump in the partial load range.
In single operation, due to the two identical pumps 2,3, it is possible to switch between the two pumps and divide the running times equally between the two pumps. In case of increased cooling demand, both electric pumps 2,3 are operated in parallel.
The presence of two pumps 2,3 of the same type creates redundancy in case of failure of one pump. If an electric pump 2,3 fails in single operation, the functional pump can replace the failed pump, as they are identical in construction. In parallel operation, if one pump fails, the functional pump can generate a reduced volume flow to cool the combustion engine. In addition, the use of two identical pumps is more cost-effective, since only one pump type has to be designed and this can be produced in higher quantities.
It is also conceivable that the pump device is used in motor vehicles. Here, too, the above-mentioned advantages result.
A rotational symmetry axis A passes perpendicularly through the center of the base of a first pump working space 11a. A rotational symmetry axis B extends perpendicularly through the center of the base surface of a second pump working chamber 11b. The first pump working space 11a is surrounded by a first sealing surface 12a on the pump side of the adapter housing. The second pump working space 11b is surrounded by a second sealing surface 12b on the pump side of the adapter housing. The sealing surfaces 12a, 12b define planar contact surfaces so that a respective planar sealing surface of a flange of an electric pump can be brought into contact with a sealing surface 12a, 12b. Thus, an electric pump can be connected to a respective pump working chamber 11a,11b. The electric pumps not shown are preferably identical. However, it may also be provided that two different electric pumps, in particular a main pump and a secondary pump, are connectable to the pump working spaces 11a, 11b. On one edge, the pump side 9 is defined as a mounting flange 13 with which the adapter housing 7 can be connected to an internal combustion engine 8. The fastening flange 13 includes recesses 14a-14f through which, for example, fastening screws (not shown) can be guided to fasten the adapter housing 7 to the internal combustion engine 8. As shown in
In parallel operation of both electric pumps connected to the pump working spaces 11a,11b, the coolant flows from the internal combustion engine 8 into the adapter housing 7 through the suction flange 15 which is connected to the internal combustion engine 8, flows through the suction port 20 and splits to the two suction pipes 21a,21b downstream of the suction port 20. The coolant is drawn towards the pump working spaces 11a,11b. The impellers (not shown) of the electric pumps force the coolant radially to the axes of rotational symmetry A, B into the discharge lines 22a,22b. The coolant flows along the two discharge lines 22a,22b until the coolant is recombined downstream of the discharge lines 22a,22b in the discharge port 23. The coolant exits the adapter housing 7 through the discharge flange 17 and flows back into the internal combustion engine 8. During individual operation of the electric pumps connected to the pump working chambers 11a,11b, the backflow flow valve 5 is in the shut-off position. Accordingly, the coolant flows only through the released suction line 21a.
While example embodiments of the present disclosure have been described above, it is to be understood that variations and modifications will be apparent to those skilled in the art without departing from the scope and spirit of the present disclosure. The scope of the present disclosure, therefore, is to be determined solely by the following claims.
| Number | Date | Country | Kind |
|---|---|---|---|
| 102020130553.2 | Nov 2020 | DE | national |
