Patent Application
20210324852
The present invention relates to the technical field of devices for providing a flow and in particular relates to gear pumps.
A gear pump uses a meshing of gears to generate a flow. A gear pump may for instance comprise a casing, wherein the casing houses a pump chamber and two or three toothed elements intermeshed for forming the gears. One of the toothed elements is a toothed wheel which is mounted on, or close to, one end of a main shaft. This toothed wheel comprises teeth extending outward from the wheel. The main shaft has the other end extending out of the casing. A rotating means, e.g. a motor, is connected to the other end for rotating the main shaft with respect to the rotating means. Driving the rotating means then generates the flow. A flow rate of the flow is determined by the rotation frequency of the main shaft and a hydraulic displacement, which is defined as the volume of fluid pumped per revolution of the main shaft.
The other toothed element, or elements, may also be a wheel, or wheels, with teeth extending outward. In this case, the gear pump is an external gear pump, and each of the other toothed wheel or wheels is mounted on a respective additional shaft. Alternatively, the other toothed element is formed as a ring having teeth extending inward. In this case, the gear pump is an internal gear pump.
A flow rate can be controlled by controlling the rotational speed of the rotating means.
US 2018/223839 A1 describes a variable displacement pump with a fixed gear, a movable gear, a fixed gear ring fitted over the movable gear, a movable gear ring fitted over the fixed gear, a fixed cover having a hole in which the fixed gear ring rotates, a movable cover having a hole in which the movable gear ring rotates, a fixed gear block attached to the fixed cover, and a movable gear block attached to the movable cover. The movable gear, together with the movable cover, the movable gear, and the movable gear block, move along the direction of the shaft to change a width in which the fixed gear is engaged with the movable gear.
US 2009/088280 A1 relates to a variable displacement gear pump device in a housing that provides variable hydraulic displacement without diverting pressurized fluid back to the pump inlet. A variable-speed pump is known from U.S. Pat. No. 10,072,676 B2. The pump comprises a proportional control valve assembly, and an actuator for controlling a load. A controller establishes a speed and/or torque of the pump and a position of the proportional control valve assembly. Further prior art useful for understanding the background of the present invention is disclosed in U.S. Pat. No. 10,138,908 B1 and US 2014/056,732 A1.
Embodiments of the present invention concern a device and a method according to the independent claims for enabling a fast variation of a flow rate without affecting a rotation speed of a main shaft. Further embodiments of the invention are specified in the dependent claims. Subsequently described aspects are to be considered embodiments of the invention if and only if they fall in the scope of any of the independent claims.
According to an aspect, a device for providing a flow rate comprises a gear pump. The gear pump comprises a casing and a main shaft. One end of the main shaft is configured to be drivingly connected to a rotating means. The gear pump further comprises, housed by the casing, a toothed wheel and at least one other toothed element intermeshed with the toothed wheel. The other end of the main shaft is connected to one of the toothed wheel and the casing. The main shaft is configured to be rotated with respect to the rotating means around an axis defined by the main shaft for rotating the toothed wheel and the at least one other toothed element relative to the casing for generating a flow. The other one of the casing and the toothed wheel not connected to the main shaft is configured to be rotated with respect to the rotating means around the axis defined by the main shaft for varying a flow rate of the generated flow.
In this aspect, the main shaft can be rotated at constant speed, and the generated flow rate can still be varied by rotating the other one of the casing and the toothed wheel not connected to the main shaft.
The toothed wheel may be mounted on the one end of the main shaft. A further toothed wheel may be mounted on a further shaft and have outward extending teeth. In this case, an outer surface of the casing may comprise outward extending teeth intermeshed with the teeth of the further toothed wheel.
Alternatively, the further shaft may be connected to the other one of the casing and the toothed wheel not connected to the main shaft. The further shaft then may be aligned with the main shaft. The further shaft then may extend opposite to the main shaft.
The device may further comprise controlling means and energy recuperation means. The energy recuperation means may be connected to the further shaft for recuperating energy from a rotation of the other one of the casing and the toothed wheel not connected to the main shaft. The controlling means may then be configured to: control an amount of energy recuperated by the energy recuperation means for varying the flow rate. Optionally, the controlling means may be configured to: receive a control signal for varying the flow rate and control an amount of energy recuperated accordingly.
The device may comprise an outer casing housing the casing, and the casing can be rotated with respect to the outer casing. In this case, an end of the further shaft may extend out of the outer casing.
An inlet and an outlet may be provided in the outer casing. Two parallel circumferential notches may be provided in a circular cylindrical surface of the casing. Two radially extending tubular channels may be formed in the casing, additionally. The radially extending channels may extend in opposite directions and may be connected to the two parallel circumferential notches. A circumferential sealing may be provided between the notches, and a pair of further circumferential sealings may enclose the notches. The notches, together with the outer casing, the sealing and the further sealings, may form tubular channels. Then, one of the notches is in fluid connection with the inlet and the other of the notches is in fluid connection with the outlet.
According to another aspect, a method for using the device comprises: Rotating the main shaft relative to the rotating means for rotating the toothed wheel and the at least one other toothed element with respect to the rotating means around the axis defined by the main shaft to the casing for generating a flow, and rotating the other one of the casing and the toothed wheel not connected to the main shaft with respect to the rotating means around the axis defined by the main shaft for varying a flow rate of the generated flow.
The method may comprise using the controlling means for controlling the amount of energy recuperated by the energy recuperation means for varying the flow rate.
The present invention provides a device configured for a quickly variable flow rate which is simple in its design and cheap to manufacture.
In the following, the present invention is explained by means of exemplary embodiments showed in the attached figures and drawings, in which
The present invention is defined by the independent claims. In the following description, reference is made to the accompanying drawings, which form part of the disclosure and in which are shown, by way of illustration, exemplary aspects by which the present invention may be realized. It is understood that other aspects may be utilized and structural or logical changes may be made without departing from the scope of the appended claims. The following detailed description, therefore, is not to be considered to limit the present invention.
The device 100 is configured for variable flow rate and comprises a gear pump. The gear pump exemplarily comprises a casing 110 with an inlet 240 for a fluid to be pumped and an outlet 250 for the pumped fluid and a main shaft 130. The main shaft 130 has one end extending out of the casing 110, for instance through an opening provided in a sidewall of the casing 110. A toothed wheel 131 with outwardly extending teeth is mounted on the main shaft 130 on, or close to, the other end of the main shaft. The toothed wheel 131 is housed by the casing 110 encapsulated in a pump chamber of the gear pump. The casing 110 further houses another toothed element intermeshed with the toothed wheel 131, for instance an other toothed wheel 141, encapsulated in the pump chamber.
In the embodiment shown, the other toothed wheel 141 has teeth extending outward and is mounted on an additional shaft 140 which extends parallel to the main shaft 130. However, the other toothed element may be formed as a ring or a belt having teeth extending inward. In this case, the one of the toothed wheels is located inside the ring or inside the belt and the other toothed element is not necessarily mounted on any shaft.
The main shaft is configured for being drivingly connected to a rotating means (not shown), for instance a motor. A flow through the casing from the inlet to the outlet can be generated by rotation of the main shaft. A flow rate of the flow is defined by a rotation frequency of the main shaft and a hydraulic displacement of the gear pump. The hydraulic displacement corresponds to the volume pumped per revolution of the main shaft.
A further toothed wheel 170 is mounted on or close to one end of a further shaft 150. The casing 110 is formed with teeth 115 extending from the circular cylindrical surface. The teeth 115 extending from the circular cylindrical surface of the casing 110 are intermeshed with the teeth of the further toothed wheel 170.
By rotating the further shaft 150, the casing 110 can be rotated around an axis defined by the main shaft 130 with respect to the rotating means. Likewise, the further shaft 150 can be rotated by rotating the casing 110 around the main shaft 130. Then, energy can be recuperated from the further shaft 150. By controlling the amount of energy recuperated from the further shaft, the flow rate can be controlled and varied.
An outer casing 160 houses the casing 110. The further toothed wheel 170 is encapsulated by the outer casing 160, and the other end of the further shaft 150 extends out of the outer casing 160. By rotating the casing 110 relative to the rotating means connected to the main shaft, the further shaft 150 is rotated relative to the rotating means and, hence, relative to the outer casing 160. Rotating the further shaft 150 relative to the rotating means causes the casing 110 to be rotated relative to the rotating means and relative to the outer casing 160.
A gear ratio between the further toothed wheel 170 and the casing 110 may be i.
If the main shaft rotates at a frequency N1>0 with respect to the rotating means and the further shaft does not rotate with respect to the rotating means, the relationship between the flow rate R, measured in m3·s−1, and N1, measured in s−1, may be represented by the bold line in
If, however, the further shaft rotates with respect to the rotating means at a frequency N2>0 in the same direction of rotation of the main shaft with respect to the rotating means, in the embodiment of
If the further shaft rotates at a frequency N3>0 in the opposite direction to the main shaft, the flow rate corresponds to rotation of the main shaft at N1−N3/i. In this case, the relationship between the flow rate R and N1 may be represented by the dashed line in
When the further shaft rotates in the opposite direction to the main shaft, it may be driven by the casing, and energy can be recuperated from the other end of the further shaft, for instance by connecting it to a motor-generator such as a dynamo.
By controlling a rate of energy recuperated from the further shaft, a flow rate of the flow generated by the main shaft may be controlled.
More generally speaking, energy recuperation means may be connected to the further shaft and may be configured to recuperate energy from rotation of the further shaft for varying a displacement generated by rotation of the main shaft.
There are two pump supply lines, one for supplying the fluid to be pumped and one for diverting the pumped fluid. Each of the pump supply lines comprises a radially extending tubular channel 200 in the casing 110. The radially extending channels 200 extend from the pump chamber in opposite directions and connect the pump chamber with two parallel circumferential, or annular, notches 210, 220 in the circular cylindrical surface of the casing 110. Corresponding to the notches 210, 220 in the casing 110, there is a circumferential, or annular, sealing 232 between the notches 210, 220.
Furthermore, a pair of further circumferential sealings 231, 233 enclose the notches 210, 220. Alternatively, the sealings may be provided in the outer casing 160. The notches 210, 220, together with the outer casing 160 and the sealings 231, 232, 233, form tubular channels. Each of the circumferential notches 210, 220 is in fluid connection with a corresponding inlet 240 or outlet 250 of the gear pump formed in the outer casing 160. There may be corresponding notches in the outer casing which correspond to the notches in the casing and are in fluid connection with the inlet or outlet.
The method showed in
The method may comprise generating a flow through the device with a predetermined flow rate and reducing the flow rate of the generated flow to a target flow rate, for instance by recuperating energy from a rotation of the further shaft, for instance by means of a dynamo.
In
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2020 204 911.4 | Apr 2020 | DE | national |
