Patent Application
20190063419
The invention relates to a diaphragm pump for the pneumatic high-pressure delivery of 1 to 10 MPa fluidized dusts, and to a method for operating a diaphragm pump of said type.
For low-pressure applications in the range of approximately 0.1 to 0.2 bar pressure elevation, use is made in practice of delivery screws with slight bulk material compression and subsequent gas injection for pneumatic bulk material delivery, see DD000000081606A1, DE000003035745A1, DE000000656009A, DE000000650988A, DE000000615779A, DE000000596565A, DE000000568999A, DE000000551066A, DE000000485635A, DE000000449676A, DE000000427455A. For somewhat higher pressures up to approximately 0.3 MPa, use is instead made of screw cellular wheels, see DE102009016191B4, DE102009016191A1. If multiple dust pumps are connected in series, it is possible to achieve correspondingly higher pressures, which is however associated with very high outlay in terms of apparatus for high-pressure applications, see DE102008049542B4, DE102008049542A1, DE102008007033A1, WO002010037601A1, WO002009095290A3, WO002009095290A2. In addition to this functional principle of the screw conveyors and cellular wheels, use is also made of dust pumps based on the principle of compressed-air diaphragm pumps, wherein, in this case, too, only low pressures are possible, DE 3909800 A1.
Whereas dust pumps are industrially used for low pressures, nowadays only lock processes have become industrially established for high-pressure processes in the range from 1 to 10 MPa, see DE102005047583B4, DD147188A3, DE102008052673A1. To reduce the investment and operating costs of such lock systems, dust pumps for high-pressure applications are also being developed, wherein the following methods are known:
For high-pressure applications in the range from 1 to 10 MPa, dust pumps based on the principle of the extrusion press are known. Here, the bulk material is mechanically compacted, as in an extrusion press, in a tapering channel to form a briquette, and thus a high pressure barrier composed of channel and briquette is formed, which is necessary for the sealing between high-pressure part and low-pressure part, see US00/0008851406B2, US02/0100021247A1. A disadvantage here is the high level of wear owing to the high acting friction forces, and the problem that the mechanical bulk material characteristics are significantly changed by this process, because, downstream of the pump, the bulk material is present in the form of briquette-like bulk material agglomerations. In particular for consumers such as dust combustion or dust gasification systems, renewed grinding under pressure is then necessary, which constitutes a hitherto unresolved problem.
Aside from the principle of the extrusion press, the piston pump principle is also known for high-pressure applications. Embodiments known in this regard are described in DE000001008201A, DE000001175653A, DE000002722931A1, DE102008009679A1. A major disadvantage here is the high, hitherto unresolved, level of wear to the dry-running piston rings. This problem can be solved through the use of diaphragms as presented in DE102011007066A1.
Here, however, owing to the gravity-driven filling process—as is also the case in all other known dust pumps and lock systems—relatively large cross sections and dimensions are necessary.
The invention is based on the problem of specifying a pump head for the pneumatic high-pressure delivery of fluidized bulk material, and a method for operating the pump head, in the case of which the bulk material is kept in a loosened, fluidized state throughout the entire pumping process.
The problem is solved by means of a diaphragm pump for the pneumatic high-pressure delivery of fluidized dusts, and by means of a method for the operation of a diaphragm pump of said type.
In the case of the dust pump according to the invention, the filling is performed by pneumatic induction, wherein the bulk material is kept in a loosened, flowable state throughout the entire pumping process, and instances of dust compaction are avoided in targeted fashion. Here, a highly compact and thus economical design is realized.
The pneumatic induction has numerous crucial advantages in relation to known dust pump systems: the cross section of the suction line 17 and thus the size of the inlet valve 8 and of the port on the pump head are much smaller in relation to a case of gravity-driven filling, whereby the pump head can be designed to be correspondingly smaller. Furthermore, the filling of the dust chamber can take place from below. This has the advantage that the construction of the pump head in the region of the diaphragm and in the hydraulic region is simplified, because there is no need for a dust leadthrough from above, which would otherwise be the case with gravity-driven filling. It is furthermore possible for the dust pump to be positioned adjacent to rather than below the hopper 11, which in turn saves structural height and increases the economy of such installations. Finally, by means of this arrangement, it is possible to realize a very large loosening surface 4 in terms of construction, which is necessary for the avoidance of instances of dust compaction and for short cycle times.
The pressure intensifier illustrated in
A further advantage of the method as a whole is that the high-pressure gas demand is yet further reduced in relation to the system described in DE102011007066A1, because firstly the dead volume that still has to be expanded after the delivering-out process can be designed to be yet smaller owing to the smaller pipeline cross sections, and secondly, during the delivering-out process, the previously supplied charging gas is jointly utilized for the pneumatic delivery.
In a further embodiment, multiple pump heads operate in a phase-offset manner with respect to one another. The delivery process is homogenized by means of this measure.
In a particular embodiment, the diaphragm is mechanically guided by means of one or more pistons or else guide rods 10, whereby undesired deformations of the diaphragm are avoided. By means of the position of the piston or of the guide rod 10 relative to the housing 9, a position measurement of the diaphragm 3 is realized.
Advantageous refinements of the invention are specified in the subclaims.
The invention will be discussed in more detail below as an exemplary embodiment, to an extent required for understanding, on the basis of figures, in which:
In the figures, the same reference designations are used to denote identical elements.
The dust pump according to the invention and the method implemented therewith are suitable for fine-grain bulk materials or dusts which can be loosened and fluidized by means of a feed of gas, such as for example carbon dust, and is directed in particular to the provision of a supply to pressurized carbon dust gasifiers with dry carbon dust infeed. Here, the process pressures lie in the range from 1 to 10 MPa. The method may however basically also be used for all other processes where it is sought to pump fluidizable dusts to high pressure in dry form.
In the case of the pump head as per
In step A), liquid is withdrawn from the hydraulic chamber, whereby the diaphragm is pulled upward and negative pressure is generated in the dust chamber. In this way, dust is drawn out of the hopper 11. It is assumed that the dust is situated in the hopper in a fluidized state by means of a feed of gas. During the pneumatic delivery into the dust chamber 1 by deflection of the diaphragm 3, a negative pressure is generated in the dust chamber 1, whereby the delivery is assisted.
When the diaphragm has reached the upper end position, then in step B), by closure of the inlet fitting 8 and by means of a feed of gas via the gas ports 5, the dust chamber is charged to the pressure defined by the pressure of the consumer 20 plus the pneumatic delivery pressure loss between pump head 14 and consumer (approximately 0.1 to 1 MPa).
In step C), for the delivering-out process, the outlet fitting 7 is opened, and the dust is, with a feed of gas, delivered out via the gas ports 5. At the same time, the volume of the dust chamber is reduced by means of the diaphragm 3 as a result of a feed of hydraulic liquid via the hydraulic port 6 into the hydraulic chamber.
In step D), the structurally inevitable residual volume of the dust chamber is expanded, and the pump cycle begins again from the start with step A).
During the induction of the bulk material, the pressure in the dust chamber 1 lies approximately 0.01 to 0.08 MPa below the pressure in the hopper 11 (delivery pressure differential). In a particular embodiment of the invention, the negative pressure in the dust chamber 1 is generated by virtue of negative pressure being applied via the gas port 5. Here, during the pneumatic delivery of dust into the dust chamber, the delivery pressure differential is generated by means of the evacuation of the dust chamber by means of a vacuum pump. The negative pressure applied via the gas port (5) is equal in magnitude to the delivery pressure differential, or is equal in value to the delivery pressure differential.
Since an individual pump head 14 operates on a batch-by-batch basis (discontinuously), multiple pump heads are interconnected, as illustrated in
An entrained-flow gasifier is supplied with 100 t/h of carbon dust at 5 MPa gasification pressure. The pressure loss between dust pump and gasifier is 1 MPa, whereby the delivery pressure is 6 MPa. The dust pump system is equipped with n=10 pump heads. One pump head thus delivers 10 t/h. The cycle time of a pump head amounts to 20 seconds, whereby a required volume of the dust chamber is determined as 0.15 m3, and the intake volume flow is determined as 270 m3/h. The hydraulic assembly operates with an operating pressure of 30 MPa and with a volume flow of 54 m3/h. Since further gas is fed during the charging and delivering-out process, the pressure delivery volume flow corresponds to 300 m3/h. The result is a high-pressure gas requirement of approximately 16,000 Nm3/h. This corresponds to an electric drive power of the gas compressor of approximately 2.36 MW. For a conventional lock system, approximately 2.3 times these values, specifically 36,800 Nm3/h and 5.43 MW of compressor power, would be necessary. With an efficiency of the hydraulic assembly of 80%, the electrical power consumption of the dust pump is determined as 0.5 MW. In this example, with the dust pump process proposed here, 2.57 MW of electrical energy, or 20,800 Nm3/h of high-pressure delivery gas, is saved in relation to a conventional lock system.
In a particular refinement of the invention, the fittings, specifically the outlet valve 7 and the inlet valve 8, are provided in a wear-resistant design.
In a particular refinement of the invention, the charging or discharging of the dust chamber 1 with gas takes place via a large-area, gas-permeable loosening surface 4 which is impermeable to the bulk material in dust form.
In a particular refinement of the invention, a large-area, gas-permeable loosening surface 4 is integrated on the base of the dust chamber 1, through which loosening surface the inlets and outlets of the dust to be delivered pass.
In a particular refinement of the invention, the loosening surface is selected to be as large as possible in relation to the inner surface of the dust chamber (at least 30% of the inner surface of the dust chamber), whereby lower gas speeds in the bulk material are realized, and a compression of the bulk material is avoided.
In a particular refinement of the invention, during the delivering-out of the bulk material, the pressure in the dust chamber lies approximately 0.1 to 1 MPa above the pressure of the receiving vessel or else dosing vessel 20.
In a particular refinement of the invention, the hydraulic system is divided into primary hydraulics and secondary hydraulics, wherein the primary hydraulics are connected to the diaphragm 3 and the secondary hydraulics are driven by means of a pressure intensifier. The pressure intensification ratio (primary pressure/secondary pressure) may be approximately 2 to 30. The primary and secondary hydraulics may be operated with different hydraulic fluids. The pressure intensifier may be designed as a pressure intensifier piston. The pressure intensifier may be designed to be resettable by means of a resetting spring, wherein the resetting spring may be designed as a mechanical spring or as a pneumatic gas pressure spring.
In a particular refinement of the invention, at least two pump heads are combined to form a system, the pressure delivery lines 18 of which are merged 19, which permits an uninterrupted delivery of bulk material.
In a particular refinement of the invention, a suction delivery line 17 proceeds from the hopper 11, which suction delivery line branches to multiple pump heads.
The present invention has been discussed in detail on the basis of specific exemplary embodiments for illustrative purposes. Here, elements of the individual exemplary embodiments may also be combined with one another. The invention is therefore not intended to be restricted to individual exemplary embodiments, but is only intended to be limited by the appended claims.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2016 201 182.0 | Jan 2016 | DE | national |
This application is the US National Stage of International Application No. PCT/EP2016/081838 filed Dec. 20, 2016, and claims the benefit thereof. The International Application claims the benefit of German Application No. DE 102016201182.0 filed Jan. 27, 2016. All of the applications are incorporated by reference herein in their entirety.
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2016/081838 | 12/20/2016 | WO | 00 |
