WO2016037655A1

WO2016037655A1 - Displacing device

Info

Publication number: WO2016037655A1
Application number: PCT/EP2014/069431
Authority: WO
Inventors: Jürgen GAYDOUL
Original assignee: Gaydoul Jürgen
Priority date: 2014-09-11
Filing date: 2014-09-11
Publication date: 2016-03-17
Also published as: BR112017004768A2; US20170276123A1; CA2960908A1; EP3060800B1; ES2687955T3; EP3060800A1; EP3181902A1; CN107076125A

Abstract

The invention relates to a displacing device for fluids, in particular liquids, which displacing device has linearly movable displacing elements, which plunge into pump chambers and are connected to crank pins of an externally driven crankshaft by means of one connecting rod each, wherein at least two groups of displacing elements are provided. All groups have the same number of displacing elements, and the crank pins for the displacing elements are arranged in such a way that said crank pins are distributed around the crank shaft at identical angular distances. The crank pins associated with a group are arranged around the crank shaft in such a way that said crank pins are offset in relation to the crank pins of the other group by an offset angle ß. Furthermore, the displacing elements of each group are arranged at an offset in relation to the displacing elements of the other groups in the axial direction of the crankshaft, and the group displacing elements are arranged at a group offset angle γ to each other around the crankshaft. The displacing device enables low pressure pulsations.

Description

Displacement device

The invention relates to a displacement device for fluids, in particular liquids, with displacers, which dive linearly in the displacer, namely in cylindrical see pump chambers in a pump housing, which are each via a suction valve and a pressure valve in flow communication, wherein the displacer each via a connecting rod are connected to crank pin of a foreign-driven crankshaft.

There are known positive displacement pumps, with which water can be brought to pressures of several hundred bar. Such pressurized water is used, for example, for descaling rolled steel billets or strips to obtain rolled products of high, uniform surface quality.

When using displacement pumps with linearly movable displacement bodies, also referred to as plungers below, pressure pulsations inevitably occur which should be kept as small as possible in order to ensure the desired uniformity of the descaling of the rolled products. In conventional positive displacement pumps, the cylinders for the displacer are arranged in series in the pump housing. Investigations by the applicant have shown that in such a series arrangement the pressure pulsations become smaller with increasing odd number of cylinders than with an even number of cylinders. The use of a large odd number of cylinders, e.g. seven cylinders, but stand against the great length, the poor mass balance and the uneven load on the crankshaft. The invention has for its object to provide a displacement device of the type described above, which leads to low pressure pulsations.

This object is achieved by claim 1, wherein for a displacement device according to the invention at least two groups of displacement bodies are provided,

all groups each have an equal number of displacement bodies, the crankpins for the displacement bodies are arranged at equal angular intervals α distributed around the crankshaft,

the crankshaft journals associated with one group are arranged offset from the crankshaft by an offset angle β to those of the other groups,

the displacers of each group are arranged offset in the axial direction of the crankshaft to those of the remaining groups, and

the group displacer are each arranged at a group offset angle γ to each other about the crankshaft.

A particularly compact construction can be achieved if two groups of displacement bodies are provided and the displacement bodies of one group are arranged alternately in the axial direction of the crankshaft with the displacement bodies of the other group.

In this arrangement, it is possible to provide the displacer in V or Boxer arrangement. With regard to a better compensation of the mass forces is advantageous if the two groups displacer are arranged in a boxer arrangement, wherein the group offset angle is 180 °, but may also be modified, for. B. may be 150 °. In a boxer arrangement, the stress on the crankshaft is minimized compared to a series arrangement with an odd number of displacers.

In a displacer device according to the invention designed with two displacer groups, each group has three displacers distributed in each case at an angular distance α of 120 ° around the crankshaft. In this case, an offset angle β of 30 ° of the crank pin associated with the first group leads to a particularly low pressure pulsation to those of the second group.

The stated object can also be solved by a displacement device of the type described above, in which a drive is provided with two opposite output shaft ends, to each of which a crank shaft of a positive displacement pump is coupled, which in each case has a group displacer,

the two groups of displacement bodies have the same number of displacement bodies,

the crankpins for the displacers of each group are offset at equal angular intervals α relative to each other about the associated crankshaft, and

the crankpins of one group are offset from those of the other group by an offset angle β about the associated crankshaft.

Further advantageous embodiments of the invention with a common drive for two positive displacement pumps are specified in the subclaims 7 to 12. The invention is explained in more detail below with reference to schematic drawings with further details. Show it:

Fig. La and lb the side view and end view of a crankshaft attached thereto two groups of three displacers in Boxer arrangement with a group offset angle γ of 180 ° in a positive displacement pump according to the invention;

2 shows the front view of a modified positive displacement pump according to FIG. 1a, but here with a group offset angle γ of 150 °;

3 shows the crankshaft according to the figures 1 or 2 without displacer in side view.

Fig. 4 and 5 are two schematic representations of the crankpin assemblies of the crankshaft of Figure 2, and that

Fig. 4, the crank pin assembly of a first group of three displacers and

FIG. 5 shows the crank pin arrangement of the second group of three displacement bodies rotated by an offset angle β; FIG.

Fig. 6a, b and c examples of the crank pin positions of a positive displacement pump according to

Figure la, lb and 2 in three different rotational positions of the crankshaft; 7 shows an arrangement according to the figures la and lb three superimposed diagrams in each case over a crank angle between 0 and 360 °, namely in the upper diagram six speed curves for the speed of the six displacer, in the middle diagram, the conveyor volumes and in the bottom diagram the pressure pulsations;

Figure 8 is a perspective view of parts of another displacement device according to the invention with a common drive for two positive displacement pumps.

9 is a partial view of the displacement device according to FIG. 8.

1a and 1b show, in a side view and an end view, a crankshaft 10 with two opposing groups A, B mounted thereon of displacers or plungers 1, 3, 5 (group A) and 2, 4, 6 (group B). The plungers of the group A are alternately arranged to those of the group B in the axial direction of the crankshaft, as can be seen from Fig. La. The groups A and B are arranged offset by a group offset angle γ of 180 ° in a boxer arrangement to each other. The angle γ is 180 ° according to FIGS. 1a and 1b, but may also deviate therefrom.

The crankshaft 10 and the plunger 1 to 6 form part of a positive displacement pump whose housings and other parts are not shown; However, it is understood that the plunger 1 to 6 in cylindrical pump chambers of conventional design are guided slidably and sealed, the pump chambers are connected via a respective suction valve and a pressure valve in flow connection to bring a fluid, for example water, to high pressures. 3 shows the crankshaft 10 alone. At its right in Fig. 3 end, it is provided with a drive pin 17, with which it can be coupled with an output shaft, not shown, of a drive, such as an electric motor. Further, it has two spaced bearing collars 18, 19, with which it is rotatably mounted in bearings, not shown, of the pump housing. In the distance between the two bearing collars crank pins 11 to 16 are arranged side by side in the axial direction. The three crankpins of the two groups are each distributed at an angular distance α = 120 °. Reference numerals 1 to 6 for the Plunger not shown in Fig. 3 relate here to the assignment to the associated crank pin 11 to 16, so l to ll, 2 to l2, etc. At this crank pin plungers are 1 to 6 via connecting rods 20 in conventional Way connected by means of crossheads 21. The three crankpins 12, 14, 16 are shown in FIG. 5 relative to the crank pin 11, 13, 15 by an offset angle ß offset on the crankshaft. As a result, the displacement effect of the even-numbered plungers 2, 4, 6 does not coincide with that of the odd-numbered plungers 1, 3, 5, but takes place offset in time by β = 30 °. This results in the result that the pressure pulsations over the circulation of the crankshaft become uniform, as explained in more detail below. For this purpose, reference is made to FIGS. 6 a, 6 b and 6 c, as well as to FIG. 7.

6a, b and c show the crankshaft according to FIGS. 1 to 5 in the three rotational positions 0 °, 60 ° and 90 °. Similar to the illustration in FIGS. 4 and 5, the crank pins 11 to 16 are symbolized by circles, which, however, are drawn smaller here for the sake of simpler illustration than in FIGS. 4 and 5. Unlike in these figures, however, all six crank pins are here each drawn in the three Fig. 6a, 6b and 6c to make the wake of the crank pin to the offset angle ß clear. In each circle, a reference numeral 1 to 6 denoting the respective plunger is entered. Plungers with odd reference numbers 1, 3 or 5 belong to group A and feed upwards in Figs. 1a, 1b and 2, while plungers 2, 4 or 6 belong to group B and convey downwards. The square plunger symbol in the respective circle above or below the plunger reference number represents the direction of action of the plunger in question. Pressurized plungers are indicated by hatching. Plungers without hatching are in the suction stroke and are pressure-free.

In the uppermost diagram of FIG. 7, the speed curves g1 to g6 of the individual plungers 1 to 6 are shown above the crank angle of the crankshaft from 0 to 360 °, the reference to the respective plunger being identified by its reference number. So the curve gl belongs to plunger 1, the curve g2 to the plunger 2 etc.

Plunger at top dead center OT or bottom dead center UT have the speed zero, thus crossing the crank angle axis x. Here begins or ends the funding process. For example, the plunger 1 is at zero crank angle in the UT and begins to promote with increasing flow. The plunger 2 is at crank angle zero already in the delivery state with increasing flow. At crank angle 60 ° as shown in FIG. 6b, the P loungeer 3 is at top dead center OT and the speed curve g3 intersects the crank angle axis sloping, while plunger 2 reaches the maximum speed and promotes maximum. At 90 °, plunger 1 delivers maximum at maximum speed, while plunger 6 has reached 0 m / s in TDC, and so on.

The curve f in the middle diagram of FIG. 7 shows the periodic oscillation of the delivery rate 1 / min achieved with a positive displacement pump according to FIGS. 1 to 5 between approximately 1550 1 / min and 1610 1 / min.

Finally, the curve d in the lowest diagram of FIG. 7 shows the pressure pulsation of the delivered liquid, which fluctuates approximately between 375 bar minimum pressure and 400 bar maximum pressure. This represents a very low pressure pulsation, which is smaller than achievable with a conventional positive displacement pump with seven plungers in series.

FIGS. 8 and 9 show an alternative displacement device, wherein FIG. 9 shows the right half of the device according to FIG. 8 in a side view corresponding to FIG. For identical or equivalent parts, the same reference numerals as in FIGS. 1 to 6 are used in FIGS. 8 and 9.

As shown in FIG. 8, the displacement device has an electric motor 30 as a drive whose continuous output shaft (not visible) with their output shaft ends 34 are each coupled to a crankshaft 10 of its own positive displacement pump 31, 32. The result is a unit of a central drive 30 and thus aligned two positive displacement pumps 31, 32, which are mounted on the engine 30 flying. Each positive displacement pump has a plunger group A with three plungers arranged in series, namely group A with plungers 1, 3, 5 (left in FIG. 8) and group B with plungers 2, 4, 6 (to the right of the electric motor 30 in FIGS 9). All plungers 1, 3, 5 and 2, 4, 6 are each arranged in series and in a same vertical plane E. The crankpins 11, 13, 15 of the crankshaft 10 of the group A are shown in FIG. 4 in the same plane E as the plunger 1, 3, 5 are arranged. However, the crankpins 12, 14, 16 of the crankshaft 10 of the group B, as shown in FIG. 5, are offset on the second crankshaft 10 by an offset angle β = 30 °. Due to this offset can be with a displacement device according to FIGS. 8 and 9 also a lower Achieve pressure pulsation than with a conventional positive displacement pump with odd plunger number.

The invention is not limited to the embodiments shown. Thus, each plunger group of an embodiment according to FIGS. 1 to 9 can also have more than three plungers for each group. There are also more than three crankpin arrangements evenly distributed about a common crankshaft, e.g. four crankpins, which are distributed at an angular distance of α = 90 ° around the circumference of the crankshaft. The offset angle β can also be less than or greater than 30 °.

The features disclosed in the foregoing description, the claims and the drawings may be of importance both individually and in any combination for the realization of the invention in its various forms.

LIST OF REFERENCE NUMBERS

A, B Plunger group

1 to 6 displacer, plunger

10 crankshaft

11 to 16 crankpins

17 drive end

18, 19 Lagerbund

20 connecting rods

21 crosshead

α Winliel distance of the plunger of a group

Offset angle of the crankpins of one group to those of the other

group

γ group offset angle of the plunger groups

30 electric motor

31, 32 positive displacement pump

34 output shaft end

E, F level

x crank angle axis

f Flow curve

d Pressure pulsation curve

gl to g6 speed curves

Claims

claims

Displacement device for fluids, in particular liquids, with linearly movable, immersed in the displacer, displacement bodies (1 to 6) in each case via a connecting rod (20) on crank pins (11 to 16) of a foreign-driven crankshaft (10) are connected, wherein

At least two groups (A; B) displacement bodies (1 to 6) are provided, all groups each have an equal number of displacement body, the crank pin (11 to 16) for the displacement body (1 to 6) at equal angular intervals (a) around the crankshaft (10) are distributed around, the one (B) associated crank pin (12, 14, 16) to those (11, 13, 15) of the other groups (B) each offset by an offset angle (ß) about the crankshaft ( 10) are arranged,

the displacers of each group (B) being offset in the axial direction of the crankshaft (10) from those of the remaining groups (A), and the groups (A; B) displacers (1, 3, 5; 2, 4, 6) each below a group offset angle (γ) to each other about the crankshaft (10) are arranged offset.

Displacement device according to claim 1, characterized in that two groups (A; B) displacement bodies (1, 3, 5, 2, 4, 6) are provided, and that the displacement bodies (2, 4, 6) of the one group (B) in the axial direction of the crankshaft (10) are arranged alternately with the displacement bodies (1, 3, 5) of the other group (A).

Displacement device according to claim 2, characterized in that the two groups (A; B) displacement bodies are arranged in a boxer arrangement, wherein the group displacement angle (γ) is 180 °.

Displacement device according to Claims 1 to 3, characterized in that each group has three displacement bodies (1, 3, 5, 2, 4, 6) each arranged at an angular distance (a) of 120 °.

Displacement device according to one of claims 1 to 4, characterized in that the offset angle (ß) is 30 °.

Displacement device for fluids, in particular liquids, with linearly movable, immersed in the displacer Verdrängerkörpern (1 to 6) are each connected via a connecting rod (20) on crank pin (21) of a foreign-driven crankshaft (10), wherein

a drive (30) is provided with two opposite output shaft ends, to each of which a crankshaft (10) of a positive displacement pump (31, 32) is coupled, each having a group (A; B) displacement body (1 to 6),

the two groups (A; B) displacement bodies have the same number of displacement bodies,

the crankpins (11 to 16) for the displacers (A; B) of each group are arranged at equal angular intervals (a) offset from each other about the associated crankshaft (10), and

the crankpins (12, 14, 16) of one group (B) being offset from those (11, 13, 15) of the other group (A) by an offset angle (β) about the associated crankshaft.

Displacer device according to claim 6, characterized in that the output shafts and the crankshafts are aligned.

Displacement device according to claim 6 or 7, characterized in that the two groups (A; B) displacer are arranged offset at a group offset angle (γ) about the crankshaft (10).

Displacement device according to claim 6 to 8, characterized in that each group (A; B) has three displacement bodies (1, 3, 5; 2, 4, 6) which are each angularly spaced (a) from 120 ° about the associated crankshaft ( 10) are arranged distributed.

10. Displacement device according to one of claims 6 to 9, characterized in that the offset angle (ß) of the crank pin (11 to 16) of each crankshaft (10) is 30 °.

11. Displacement device according to one of claims 6 to 10, characterized in that the drive (30) is an electric motor.

12. displacer device according to claim 11, characterized in that the electric motor (30) has two opposite, mutually aligned output shaft ends (34) which form the end portions of a continuous electric motor shaft.