KR20050114270A - Pump - Google Patents

Abstract

The invention relates to a pump (1), such as a vacuum pump or a compressor, comprising a pump housing (18) and at least one pump piston (2, 3) that moves along a circular path. In order to embody a novel pump of said type, the pump piston (2, 3), which is optionally coupled in a rigid manner to one or several additional pump pistons (2, 3), moves about a swivel pin (5) so as to oscillate along a trajectory that is correspondingly provided with two reversing positions. Optionally compressed or pressurized medium is discharged via a discharge valve (8) while an intake valve (9) opens during a movement from one reversing position to the other, whereupon the medium is discharged at a given pressure end of the pump piston (2, 3) while being sucked in at an intake end thereof during a pressure build-up.

Description

Pump {PUMP}

The present invention relates to a pump having at least two pump pistons moving along a common circular path.

Many types of pumps, such as so-called vacuum pumps, are already well known. For example, while a continuous rotary radial compressor is known, a piston compressor that performs reciprocating or oscillating motion is also known.

1 is a plan sectional view of a first embodiment of the present invention.

2 is a perspective view showing two pumps connected to each other.

3 is an explanatory view showing two pumps driven simultaneously by a driving means;

Figure 3a is an explanatory view schematically showing a crankshaft connected to the drive means.

4-6 are partial cross-sectional views illustrating the sealing and valve operation of the pump piston to the housing.

7 is a sectional view showing a structure of a housing partition wall having an outlet valve;

8 is a perspective view of a partial incision display showing another embodiment.

9 is a perspective view of a housing dividing wall in which an inlet valve and an outlet valve are disposed;

10 is an exploded perspective view of the housing partition wall shown in FIG. 9;

11 is a longitudinal sectional view of a pump housing showing another embodiment of a housing partition wall with an outlet valve.

12 is a partial perspective view showing the area of the pump chamber in which the outlet valve is disposed in the housing partition wall;

FIG. 13 is a perspective view similar to FIG. 12 showing another embodiment where the rotary piston has an open protrusion associated with the outlet valve; FIG.

FIG. 14 is a sectional view similar to FIG. 4 showing another embodiment related to gap closure; FIG.

FIG. 15 is a sectional view similar to FIG. 5 showing a configuration having a closed structure shown in FIG.

16 is a cross-sectional view of the pump.

17 is a rear view of the pump shown in FIG.

18 is a perspective view of a drive housing having a pump housing separated on both sides;

19-21 are partial perspective views showing valve strips with inlet / outlet valves of another embodiment.

22-24 are respective cross-sectional views of FIGS. 19-21.

FIG. 25 is a cross sectional view of a pump similar to FIG. 16 showing that the pump housing is separate in the entire housing; FIG.

FIG. 26 is a front view of the pump according to FIG. 25 with crank drive means operating in the pump housing; FIG.

In this regard, the present invention has at least one pump piston and a pump housing that move along a circular path, the pump piston being selective for one or more other pump pistons that oscillate about an axis of rotation on a motion path having two inverted positions. The medium is discharged through the outlet valve, and during the movement from one inverted position to the other inverted position, the inlet valve is opened, and then in the pressure generation process, the medium is discharged from the pressure side of the pump piston. A new pump is sucked in on the suction side of the pump piston.

Such a pump can, for example, achieve a higher power than a radial compressor. In this case, the pump has a relatively simple structure.

Claims The dependent claims of the invention are described below by reference to the subject matter of Claim 1, but each of which is also important.

In one configuration, the inlet valve can be switched in motion from the inversion position on one side to the inversion position on the other side.

The pump pistons move in the pump chamber. The pump chamber is formed radially inward by an inner wall fixed to the pump piston. Where multiple pump pistons are provided, a connecting wall is preferably provided between the two or more pump pistons. The housing wall surrounding the pump chamber radially from the outside is suitably fixed. However, as will be described in detail later, this housing wall may be configured to be movable. Inlet valves may be formed on the bottom or top surface of the pump chamber, or on the housing outer wall or housing partition wall.

The pump chamber is enclosed in the direction of movement of the pump piston on both sides by a fixed housing partition wall. In the case of two pump pistons, the housing dividing wall divides the two pump chambers. This housing partition wall allows the required degree of pressure to be created when the pump piston moves to the inverted position. The outlet valve is preferably configured in the form of a check valve. The outlet valve may be configured on the housing dividing wall or on the bottom of the pump chamber or on the top of the pump chamber or on the outer wall of the housing.

The pump may for example be driven by an electric motor. However, the pump can be driven by other types of prime movers. As will be described later in detail, a crankshaft is preferably used for power transmission.

The motor may also be an electric motor that directly generates a reciprocating motion. In this case, the electric motor may be a particularly common universal motor. However, this motor may be a so-called reluctance motor. It is suitable that a stepping motor is used for example to directly generate the reciprocating motion. It is also possible, for example, to provide an electric or electromagnetic spring / mass flywheel system as drive means. The mass flywheel is for equilibrium.

What is important here is the arrangement of the drive shaft and the pump, for example when two pumps with one central drive shaft are connected to each other. Although the inverted positions of the pistons of the two pumps are in phase, the angular position is different in the intermediate position and the upper deviation may vary depending on the position of the center point. This can be minimized by careful height setting between the drive shaft and the pump.

When the driving force is transmitted to the pump by the crankshaft, it is advisable to drive two or more such pumps simultaneously. The crankshaft allows the motor, in particular the electric motor, to carry out a continuous movement. Reciprocating motion in a limited angular range of a pump or pump piston can be obtained by connecting rods operating on known crankshafts, such as in the case of gasoline or diesel engines for vehicles. Two pumps of this type are preferably driven in opposite directions by the same crankshaft.

Particular attention should be paid to the sealing of the pump in the pump housing. Such a seal may be provided, for example, in the region of interaction with the outer partition in the peripheral direction and the housing partition wall in which a suitable seal can be achieved along the length of the gap between the inner region in the peripheral direction, for example, formed therebetween. Is provided. This gap ranges from one hundredth of a millimeter or one tenth of a millimeter. In particular, this gap is in the range of a few hundredths of a millimeter.

However, separate seals may be used on these areas or on one or more surfaces that are in tightly interacting surfaces or on cladding surfaces where at least one of the surface areas interacting with each other in the course of operation of the pump.

Reciprocating or oscillating movement of the piston is performed without contact with the housing dividing wall. In the inverted position, each pump piston stops a few tenths of a millimeter forward in the housing dividing wall, or a few percent or tens of minutes relative to the range of rotation angle that the pump piston passes through in the movement from one inverted position to the other inverted position. Stop one percent ahead.

In particular, the housing partition wall is formed in a radial direction at a constant distance from the piston region in the range of the peripheral angle of the maximum approximation value. However, this distance may be selected such that a wide gap can be formed outwardly (radially direction) of the wedge shape (straight surface area) between the areas where the pump piston stops.

The angle of rotation of the piston is about 90 degrees. However, it may include more than or less than, for example, the range of + /-30 ° and may include the middle range, such as 95 °, 100 °, 105 °, 110 °, and may have an angular range between them. In addition, the same angular range can be applied to a value of 90 ° or less. By doing so, the respective volume of filling and piston size can be matched.

The pump piston is preferably composed of a light metal such as aluminum. More preferably, they consist of extrudates (but the material need not be aluminum). To this end, the structure is designed to carry as much mass as possible in radial positions as far away from the axis of rotation of the pump piston as possible. In addition, because of the moment of inertia, the moving mass should be as small as possible, and for this reason a lightweight material, such as aluminum, is preferably used for the moving mass.

When composed of extrudates, the pump piston has a cavity therein. These cavities are closed by a top and bottom cover.

The height of the pump piston or the axial magnitude of the common axis of rotation corresponds to the diameter from the axis of rotation to the circumferential outer wall of the pump piston. This is to minimize the gap.

The inlet valve can consist of a permanent opening in a simple form. For example, such an inlet valve may be in the form of a through hole or a request. In addition, it may be configured in the form of a check valve (for example a ball valve).

In the case of a pump with two pump pistons, four outlet valves and two inlet valves may be provided, respectively. However, for example, four inlet valves may be provided when two are turned off.

Further, the inlet valve and the outlet valve are arranged at the same end region of the motion path, that is, at each inverted position. In this case, the inlet valve and the outlet valve may be disposed adjacent to each other. In this regard, the inlet valve and the outlet valve are advantageously arranged in the same housing partition wall.

The inlet valve or outlet valve in this case consists of a perforated or curved metal sheet portion consisting of a valve plate in the form of a closed plate having a bent portion adjacent to the valve opening. In this regard, a metal sheet portion composed of steel, in particular spring steel, can be used. The inlet valve or outlet valve also has a curved portion extending in the same plane as the valve plate. They are preferably arranged without deviation from each other with respect to this plane. In addition, the inlet valve and the outlet valve have, for example, a mounting angle that is mounted in a gripping manner to an area of the housing partition wall. It is also preferred that this mounting angle extends at least partially in the common plane of the curved portion.

For the hermetic closure of the inlet valve or the outlet valve, the valve plate is preferably placed on a hermetic support which is mounted in a gripping manner between the valve and the housing part. It may also be mounted with an adhesive, for example. In the case of mounting by a gripping method, such mounting is preferably made by a clamping part or a pressing part. The support may consist of a portion consisting of a plastic, for example an elastomer.

In particular, in the case where the valve is configured in the form of a perforated or curved metal sheet portion consisting substantially of the mounting angle, the bend and the valve plate, the longitudinal extension of the inlet or outlet valve extends in the direction of the rotation axis of the pump piston. . Therefore, a plurality of outlet valves can be arranged in close proximity to each other in the direction of the rotation axis. In addition, a plurality of inlet valves may be arranged in close proximity to each other to be aligned with the rotating shaft.

The partial arrangement of the spring-tight inlet valve with respect to the outlet valve in the housing dividing wall has been found to have the advantage of reducing power consumption in the intake process, i.e., in the recharging of the pressure chamber. Therefore, the pressure difference is reduced. The valve, i.e. the inlet valve and the outlet valve, is particularly preferably composed of a tongue valve having a seal of elastomer.

The valve may also consist of a valve strip that can be easily exchanged. In such a case, simply rotating the valve strip involves switching the inlet valve of the outer side arrangement to the outlet valve of the outer side arrangement or vice versa. This allows multiple pumps to be connected in series or in parallel as required. Depending on the situation, the required valve may be arranged (rotating the valve strip) without requiring an elongated gas flow conduit. To this end, the valve strip is configured symmetrically with respect to the longitudinal axis. In each case the inlet and outlet valves are arranged opposite to the other side with respect to the central longitudinal axis of the valve strip.

The valve tongue of the tongue valve is configured symmetrically. The spring steel may be a suitable material, for example Viton (trade name). Since the valve is planar, dead space can be minimized with respect to the inverted position of the piston. The inlet valve is in the same plane as the plane of the valve strip. For the outlet valve, the wall thickness of the valve strip can be made thin and a U-shaped portion is additionally formed in the pump piston to avoid the formation of dead spaces in front of the valve element.

The pump piston has an open protrusion for triggering this outlet valve in relation to the outlet valve. If a plurality of outlet valves are arranged in close proximity to each other, the same number of open protrusions are provided in the pump piston. These raised surface elements in the pump piston interact with the outlet valve, in particular the spring valve, in the inverted position and allow mechanical opening of the outlet valve.

The pump also has three, four or more pump pistons, at least two of which move in a common circular path. In such a case, when the two circular circular paths are different, these different circular paths may be configured in different pump housings. Each pump housing may have two pump pistons capable of vibrating motion and a pump chamber separated by a housing partition wall in each pump housing.

For the four pistons constructed in the case of the above mentioned example, a common drive means is provided, which drive means is arranged in a third housing, ie a drive housing separate from the two pump housings. The drive housing also has two pump housings arranged adjacent to both sides.

The housing, ie the drive housing and the pump housing, may consist of extrudates. However, they may for example consist of castings. These housings can be joined to each other by longitudinal demands and longitudinal projections (in the direction of the rotation of the pump piston), which can be simply configured simultaneously when composed of extrudates. However, these longitudinal demands and protrusions are merely those that can assist in assembly. In addition, screwed union or adhesive bonding may be used for the connection between the housings.

In particular, when the housing consists of an extrudate, the delivery channel can be integrally formed in this housing in a simple manner. This is because it can be configured simultaneously in the housing in the form of a cavity extending in the direction of the rotation axis of the pump piston and one or both sides closed by a cover.

In order to seal the pump chamber, the pump piston or the pump housing is flooded with the surface area of the movement gap. This flocking area forms a coating layer that is removed by wear to form a minimum gap during the first operating cycle. This flocking area shows our maze effect. In this regard, of course, it is also possible to form other coatings which show their own abrasion action (they do not have to take advantage of the maze seal).

In pump pistons made of aluminum, for example, shrink-coupled steel shafts may be provided to constitute a physical axis of rotation.

The structure of the pump chamber is a quadrangle, that is, a quadrangle which forms a free path of the pump piston between the inverted positions substantially coincident with the extension of the pump chamber in the direction of the rotation axis. The aim is to minimize the gap length. It is better to follow the formula that minimizes the sum of twice the gap length and twice the difference between the outer and inner diameters of the pump chamber. Further, the structure of the pump chamber may constitute a pump chamber in which the free path of the pump piston between the inverted positions is smaller than the extension of the pump housing in the direction of the rotation axis and the free path of the pump piston is larger than the extension of the pump chamber in the direction of the axis of rotation. To help.

Referring to the present invention in more detail based on the accompanying drawings as follows.

1 shows a pump 1 having two pump pistons 2, 3 connected to each other via a common central region 4 having a basically circular cross section in the illustrated embodiment. In the central region 4, the rotation axis 5 is disposed at the center thereof, and the pump pistons 2 and 3 rotate back and forth in a vibrating manner.

During operation, the pump piston 2 (3) passes through the inlet valve 9 while moving clockwise from the position shown in FIG. 1 (first inversion position) until they reach the second inversion position. Thereafter, between the pump piston and the housing dividing wall 6, 7 until the back pressure of the outlet valve 8 reaches a preset value (or until the steel opening of the outlet valve occurs, as described later). Pressure is generated. And the pump piston reaches one side reverse position. Starting from this, they move in a direction opposite to the first direction of motion and this process is repeated in the reverse direction of rotation.

In an embodiment of the invention, the pump pistons occupying an angle range α of about 60 ° each move in an angle range of 120 °. In the region of 180 °, two housing dividing walls 6, 7 lie opposing in the pump housing 18 (shown schematically). In the embodiment according to FIG. 1, the outlet valve 8 is formed upstream of the housing dividing walls 6, 7 in the rotational direction of the pump pistons 2, 3, respectively. An inlet valve 9 is formed in the 90 ° region of the 180 ° pump chamber where the pump pistons 2 and 3 move.

In another embodiment, the pump pistons are formed in an angle range of about 90 ° so that they may each move in an angle range of 90 °. The benefit of sealing is obtained by the long sealing length. Moreover, the inlet valve does not open too long and the gas is initially not partially pushed back (in the return path).

The angular range of the piston may also be greater than 90 °. For example, it may be 110 °, 120 °, or 130 ° or an intermediate angle range thereof. And compression does not need to occur on the back side. The inlet valve is suitably arranged in the vicinity of the pump piston at the compression start position.

The outlet valve 8 is a check valve while the inlet valve 9 is simply in the form of an opening.

In Fig. 2, the double piston is shown in perspective view. The height h of the pistons 2 and 3 coincides with the radius r from the rotation axis 5 to the piston outer wall 10. Moreover, the diameter D of the central region 4 is about one third of the total diameter d of the two pump pistons 2 and 3 constituting one unit together with the central region 4.

In FIG. 3 the drive system of the two pumps 1 driven by the electric motor 11 is schematically shown. The crankshaft 12 is connected to the electric motor 11 in a flange mounting manner, and the pump pistons 2 and 3 are driven in the opposite direction through the connecting rod 13. The crankshaft 12 has an equilibrium weight or mass flywheel 14.

The arrangement shown here has the advantage that the arrangement can be made in a way that saves space while keeping the axis in a horizontal position, and all units can be built as one pump in the base area. That is, the motor and the pump may be arranged on the tower in a state where the shaft is horizontally arranged. This has the advantage that the housing can be constructed in a rectangular shape in that it provides at least two standing areas at the same time. One standing area corresponds to the arrangement of FIG. 3 and the other standing area corresponds to the arrangement area as mentioned above.

4 to 6 show in detail the gap sealing structure required for the fixed capacity pump.

In Fig. 4, the radially outer gap sealing structure of the pump piston 3 is shown. As another form of sealing structure mentioned at the beginning of the present invention, the pump piston 3 may have a sealing piece 15 according to the size of the gap, which sealing piece is firmly connected to the pump piston 3 and that the pump housing 3 It lies against the inner wall 16. For example, they can consist of plastics such as PVC, PP or PE.

Such a closure structure can also be provided radially inside. In addition, a sealing structure can also be provided between the housing partition wall and the connecting wall of the pump piston. FIG. 5 schematically shows a sealing structure between the housing partition wall 7 and the central region 4. In this case, the sealing piece 17 is firmly connected to the housing dividing wall 6 and is formed on the inner wall of the pump housing which is constituted by the central region 4 and rotatably fixed to the pump piston 2, 3. Interact in a sealed manner.

7 shows the housing partition wall 6 of another embodiment in a cross-sectional form. In the case of two housing dividing walls 6, 7 one, two or more outlet valves 8 are formed. The outlet valve 8 consists of valve plates 19 and 20 which, in the case of the illustrated embodiment, are connected to one another in the form of a U-shaped cross section and which are arranged under spring contact with respect to the through holes 21 and 22. Seals 23 and 24 having coupling holes corresponding to the through holes 21 and 922 are disposed between the through holes 21 and 22 and the valve plates 19 and 20, respectively.

The opening of the outlet valve by the generated positive pressure may also allow the outlet valve to be forcibly opened as shown in FIG. 6 when the outlet valve is disposed on the housing partition wall as shown in FIG. 7. The valve plate is pressurized in the open position in each case by an opening which is firmly connected to each pump piston. This is particularly advantageous with time control.

In this connection, it is also possible, independently, to have the side walls of the pump pistons 2 and 3 respectively contact the housing dividing walls 6 and 7 in the inverted position. Here, it is advantageous to provide a soft coating, for example foam rubber, on the housing dividing wall or on the wall of the pump piston 2, 3.

8 schematically shows another arrangement of the outlet valve 8 and the inlet valve 9. They are arranged in the region of the housing dividing wall 6 which divides the two pump chambers 25. The radially opposed housing partition wall 7 is configured identically to the housing partition wall 6.

As is shown in particular in FIG. 9, the housing dividing wall 6 consists of a hollow portion which extends and is aligned parallel to the axis of rotation 5 of the pump piston 2, 3. The cavity formed in this way is separated in the center by the horizontal wall 26. On both sides of the transverse wall 26, an outlet valve 8 and an inlet valve 9 are formed, and through-holes 21 and 22 are formed in the wall of the housing dividing wall 6 facing the pump chamber 25. have.

The inlet valve 9 and the outlet valve 8 are disposed on both sides of the housing dividing wall 6 provided with the through holes 21 and 22, respectively, and each valve is connected by the curved portion 28 regardless of its function. It has a valve plate 27 in the form of a closed plate. The valve plate 27 and the bend 28 are in one piece, which extend in a common plane and are punched out of a metal sheet, in particular spring steel. The curved portion extends to the longitudinally extending side of the housing dividing wall 6, that is to say in a direction parallel to the rotation axis 5.

At the end, ie at the end away from the valve plate 27, the bend 28 has a mounting angle 29. The spring portion of the inlet valve 9 constituted by the valve plate 27, the curved portion 28, and the mounting angle 29 is shaped like a key. However, the shape may also consist of continuous straight lines.

The spring portion 30 of the outlet valve 8 has two opposing mounting angles 29 arranged at the ends of the curved portion 28 such that these mounting angles and the curved portion 28 are T-shaped in shape. Arranged to achieve.

A membrane support 31 is arranged between the spring portion 30 and the wall of the housing dividing wall 6 to which the spring portion is coupled, which is particularly shown in FIG. 10 in the case of the inlet valve 9. Likewise has a contour that matches the contour of the spring portion 30. In addition, one side end at which the mounting angle 33 arranged at substantially right angles is disposed, and in particular in this embodiment, a through hole formed in the housing partition wall 6 having a circular ring shape and an outer diameter equal to the outer diameter of the valve plate 27. A stem 32 is provided having a closure 34 having an inner diameter equal to the diameter of 22.

The support 31 of the outlet valve 8 has a rectangular shape and is integrally formed with the sealing part 34 formed in the valve plate 27 of the spring portion 30, and the diameter of the through hole is formed in the housing partition wall ( It is equal to the diameter of the through-hole 21 of 6).

Two inlet valves 9 and outlet valves 8 are provided for each housing dividing wall 6, 7, each of which is sealed to the other side by housing dividing walls 6, 7. It is arranged toward the (25) side. Thus, the valves are arranged opposite each pair.

The spring portion 30 and the support 31 constituting the outlet valve 8, that is, the outlet valve 8, are disposed inside the housing with respect to the housing partition wall 6, and the support 31 is each spring portion. Gripping is established between the 30 and the housing part. A pressure section 35 is provided for this purpose. This pressure portion is arranged in the region of the two mounting angles 29 at intervals between the two spring portions 30 in the housing partition wall which is a hollow chamber type. Thus, a support is formed on each side for the outlet valve 8 in the form of a spring valve. It can also be glued with an adhesive instead of gripping and used together if appropriate.

The support 31 and the spring portion 30 of the inlet valve 9 are arranged in the concave inlet 36 of the same contour formed on the outer wall of each housing dividing wall 6, 7 facing the pump chamber 25, In each case the support 31 is mounted in a gripping manner between the spring portion 30 and the housing wall by a gripping portion 37. This gripping portion 37 extends on the housing dividing wall 6, 7 in the recessed portion region of the upper portion. In the gripping position, the two corner portions of the gripping portion 37, which is a C-shaped cross section, are engaged on the mounting angles 33 and 29 of the support 31 and the spring portion 30 to form an end coupling of the tongue valve.

The arrangement of the outlet and inlet valves relative to the housing partition wall allows for a small dead space and good compression.

The control of the valve is preferably made in accordance with the pressure. Thus, starting from one inverted position, negative pressure is generated by the pump pistons 2 and 3 moving in a direction away from the housing dividing walls 6 and 7, which effect exceeds the previously selected limit value. After that, the inlet valve 9 is opened. In the case of the medium compression movement of the pump pistons 2 and 3, in the direction of the housing dividing walls 6 and 7, the pressure increases so that the outlet valve 8 is opened.

The spring portion 30 of the outlet valve 8 is tipped in the direction of the pump chamber 25 and opens inwardly in the direction of the hollow chamber of the housing dividing walls 6 and 7 when the pressure exceeds the limit. . On the other hand, the spring portion 30 of the inlet valve 9 is tipped in the direction of the hollow chamber of the dividing walls 6 and 7 so that when the predetermined low pressure pressure value exceeds the limit value, The direction of 25 is bent outward to open.

As shown in the cross-sectional view of FIG. 11, a plurality of outlet valves 8 may be arranged in close proximity to the housing partition walls 6 and 7. For example, in the illustrated embodiment, three outlet valves 8 are provided for each housing partition wall 6, 7. These outlet valves 8 are constructed similarly to the outlet valves 8 mentioned above and have a spring portion 30 of a tongue valve type. These spring portions 30 of all three outlet valves 8 of the housing dividing wall 6 are constructed in one piece, and each mounting angle 29 is opened to the common base 38 side.

In this embodiment, each inlet valve 9 of each pump chamber 25 is configured in the form of a permanent opening 39 in the form of a through hole in the bottom region of the pump chamber 25 (see FIG. 12). ). The inlet valve 9 thus formed is operated during movement from one inversion position to the other inversion position.

Moreover, FIG. 13 shows another embodiment, in which the pump pistons 2 and 3 are operated in an inverted position with respect to the outlet valve 8 arranged in proximity to the housing partition walls 6 and 7. It has an open protrusion 40 for triggering the outlet valve 8. By these open protrusions 40, the valve plate 37 of the outlet valve 8 is mechanically forced open.

14 and 15 show in detail the gap closure structure between the pump piston 2 and the pump housing. For example, the pump pistons 2 and 3 are provided with a connecting layer 41 in the form of a connection layer which is worn out and removed in the first operating cycle so as to form a minimum gap in the region of the movement gap from the radially outer side. This flocking layer is also provided radially inward. For example, FIG. 15 schematically shows a sealing structure by the flocking layer 41 between the housing partition wall 7 and the central region 4. In addition, although not specifically shown, such a flocking layer is formed also in the end surface of the pump piston 2 (3). The flocking layer is a coating layer for obtaining the required sealing effect. Other coating layers may be formed.

In FIG. 16, a cross section of the pump housing G is shown. Such a pump housing consists of an extrudate such as, for example, aluminum and has a portion in which an electric motor 11 is inserted. On both sides of the electric motor 11, a pump chamber is arranged in which two pump pistons 2 and 3 are respectively moved in a common circular path. Each pump piston 2, 3 is coupled to a pump chamber 25, which is separated from each other by radially symmetrical housing partition walls 6, 7 in which the outlet valve 8 is arranged. An inlet valve 9 is formed at the end of the pump chamber 25.

17 shows the back of the pump 1. This pump has an electric motor 11 in the center, which is used to crank drive two pairs of pump pistons arranged on both sides. To this end, an extension arm 43 is rotatably mounted on the electric motor 11 or its drive shaft 42 and used to drive the connecting rod 13 to drive the pair of pump pistons in the opposite direction.

In addition, although not particularly shown, a stamping motor may be used to drive each pair of pump pistons. Electromechanical vibrators may also be used.

Finally, FIG. 18 shows another embodiment of a pump housing G consisting of three parts. Thus, the drive housing 44 and two pump housings 18 for inserting a pair of pump pistons are provided. These housings preferably consist of extruded aluminum.

The drive unit housing 44 is configured to allow the electric motor 11 to be inserted.

The two pump housings 18 are of the same shape and can be interchanged and can be arranged symmetrically with respect to the drive part housing 44. The pump housing 18 can likewise be constructed of the same extrudate.

Fixing the two pump housings to the drive housing 44 is made by means of an extruded longitudinal request 45 and a projection 46 having the same cross section as the request. In addition, this fixing may be performed by pinning, the use of a screwed union or adhesive bonding (these methods may be used individually or in combination).

In particular, the selected configuration of the pump housing 18 allows the length of the pump chamber 25 to be varied in the simplest way with respect to the axis of rotation of the pump piston, so that the structure of the pump chamber 25 is suitable for different conditions. It can be preset in the simplest form. The structure of the pump chamber should preferably be as rectangular as possible, in which case the diameter of the pump piston corresponds to the range of the pump chamber 25 in the direction of the rotation axis 5.

An accessory, such as a suction connection or a pressure connection, can be arranged in front or rear when viewed in the direction of the axis of rotation. Such an accessory may be integrally configured to be coupled to an intermediate space formed between the motor housing and the drive housing in the form of a gap, for example in the case of the illustrated embodiment.

The pump can also have separate housings and they can be inserted into the entire housing.

In selecting the material, the pump piston and the pump housing are made of the same material. If different materials are used, the pump piston is made of a material having a lower coefficient of thermal expansion than that of the pump housing.

Another embodiment of the inlet / outlet valves is shown in FIGS. 19-24.

In the case of the embodiment shown in FIG. 19, the outlet valve simply consists of a valve flap 47 disposed inside the housing partition wall 6 and a particular type of opening formed in the housing partition walls 6 and 7. The openings 48 are formed in a large number in the region of the outlet so that portions of the housing partition wall remaining between these openings have a function of supporting the valve flaps 47.

Basically, the inlet valve can also have the same structure. In order to maintain the transition area as flat as possible on the outer wall between the valve flap and the outer surface, it is desirable to make a request at the position where the valve flap lies on the outer wall.

A cross section corresponding to FIG. 19 is shown in FIG. 22. Here, it is shown that one valve flap 47 is placed at the outlet position while the other valve flap 47 is disposed against the inner wall in a sealed state.

In the embodiment of Fig. 20, a ball valve is used. 21, the outlet valve and the inlet valve are configured in the form of a combination valve. When the inlet valve opens in the inlet position, it simultaneously shows a direct coupled structure in which the outlet valve is closed in the closed position or vice versa. The active element, that is, the closing ball 53, is an active element of the inlet valve and an active element of the outlet valve.

In particular, in the embodiment shown in FIG. 20, a cage 49 having a through hole 50 in which a gas supply line (not shown) communicates with the gas discharge line is provided. This cage 49 has hermetic flanges 51 and 52 which are coupled to the housing dividing walls 6 and 7. The inside of the ball side may be covered with a sealing material such as, for example, rubber or elastomer. The cage 49 may also be integrally constructed from such a material. The closing ball 53 is accommodated in the cage 49. Depending on the pressure exerted on this closing ball, the closing ball moves to the closed position. The cage extends between the housing dividing walls 6 and 7 to connect them.

These valves require only a very small pressure difference to operate or move these valves. They operate without bias, i.e. substantially without bias. It is also against the backdrop that the above mentioned pumps or compressors are operated with a small pressure difference. In either case, volume flow is important. The pressure difference can range from one tenth or tens of bar.

21-24, the valve of the embodiment of FIG. 22 acts simultaneously as an outlet valve and an inlet valve. In particular, the valve consists of two valve plates 54, 955 which are rigidly joined by a connection 56 in the form of a rod in the illustrated embodiment. The connecting portion 56 extends laterally with respect to the housing partition walls 6 and 7. Inside the valve strip, ie at least between the housing dividing walls 6, 7, the connection 56 is connected by a spring portion 56. Thus, the connecting portion is arranged at an intermediate position in which both the inlet valve and the outlet valve are open. This allows the inlet valve or outlet valve to be moved to the closed position.

In addition, a simple tubular guide can also be provided. In particular this allows one of the valve plates 54, 955 to be arranged inwardly of the housing partition walls 6, 7 in a closed position, leaving the embodiment shown in practice.

In FIGS. 25 and 26, the pump piston is operated only in a separate housing, partly seen as the first housing 57, which is housed in the outer housing 58 and the housing 57 is rotatably housed in the housing 58. In the case of the movement of the pump piston by the crank drive shown in FIG. 26, the movement is performed by the same driving unit which drives the pump piston. The absolute motion from one inversion position to the other inversion position is for example the same (the output is the same).

In this embodiment, the housing 58 may be configured in the same manner as the multi-part configuration as described in relation to FIG. 18.

All these features (in themselves) belong to the present invention. In addition, the contents of the attached priority claim (a copy of the conventional patent application) are also included in the present invention and included in the claims of the present invention so that the features of these documents can be combined.

Claims (36)

In a pump (1), such as a vacuum pump or a compressor, it has at least one pump piston (2, 3) and pump housing (18) moving in a circular path, the pump piston (2, 3) having two inverted positions. Optionally firmly coupled to one or more other pump pistons 2, 3 oscillating about the axis of rotation 5 on the path of movement, the compressed or pressurized medium is discharged through the outlet valve 8, During the movement from the inverted position to the inverted position on the other side, the inlet valve 9 is opened, and then in the pressure generation process, the medium is discharged from the pressure side of the pump pistons 2 and 3 and the pump pistons 2 and 3 A pump, characterized in that suction on the suction side. The pump as claimed in claim 1, characterized in that the inlet valve (9) can be switched in motion from the inverted position on one side to the inverted position on the other side. The pump as claimed in any one of the preceding claims, wherein the pump chamber is radially formed inward by an inner wall fixed to the pump piston. The pump as claimed in any one of the preceding claims, characterized in that the housing wall, which surrounds the pump chamber radially from the outside, is fixedly formed. The pump as claimed in claim 1, wherein the housing wall surrounding the pump chamber radially from the outside is movable. Pump according to one of the preceding claims, characterized in that the inlet valve (9) is formed on the bottom or top surface of the pump chamber or on the housing outer wall or the housing partition wall. The pump as claimed in any one of the preceding claims, characterized in that the pump chamber is enclosed in the direction of movement of the pump piston (2, 3) on both sides by a fixed housing dividing wall. Pump according to one of the preceding claims, characterized in that the outlet valve (8) is in the form of a check valve. Pump according to one of the preceding claims, characterized in that the outlet valve (8) is configured on the housing dividing wall or on the bottom of the pump chamber or on the upper surface of the pump chamber or on the housing outer wall. The pump as claimed in claim 1, wherein the pump is driven by an electric motor. The pump as claimed in claim 1, wherein the pump is driven by a stepping motor. The pump as claimed in claim 1, wherein the pump is driven by an electromagnetic vibrating mechanism. The pump as claimed in claim 1, wherein the drive is performed by a crankshaft. The pump as claimed in claim 1, wherein the drive acts on two or more pumps connected by the same crankshaft. Pump according to one of the preceding claims, characterized in that when two pumps (1) are driven by the same crankshaft they move in opposite directions. Pump according to one of the preceding claims, characterized in that the inlet valve (9) and the outlet valve (8) are arranged in the same end region of the movement path. Pump according to one of the preceding claims, characterized in that the inlet valve (9) and the outlet valve (8) are arranged on the same housing dividing wall. Perforated or curved according to any one of the preceding claims, wherein the inlet valve 9 or the outlet valve 8 consists of a valve plate 27 having a curved portion 28 adjacent the valve openings 21, 22. A pump comprising a metal sheet portion. Pump as claimed in any one of the preceding claims, characterized in that the valve plate extends into a curved portion (28) having the same diameter. Pump according to one of the preceding claims, characterized in that the inlet valve (9) or outlet valve (8) has a valve plate (27) and a curved portion (28) extending in a common plane with each other. Pump according to one of the preceding claims, characterized in that the inlet valve (9) or outlet valve (8) has a mounting angle (29) that is mounted in a gripping manner. Pump as claimed in any one of the preceding claims, characterized in that the mounting angle (29) extends in the curved portion (28) in a common plane. Pump according to one of the preceding claims, characterized in that the valve plate (27) is seated on a support (31) mounted in a gripping manner between the valve and the housing part. Pump according to one of the preceding claims, characterized in that the mounting by gripping is achieved by the clamping part (37). The pump according to any one of the preceding claims, characterized in that the attachment by the gripping method is made by a pressurizing portion (35). Pump according to one of the preceding claims, characterized in that the longitudinal extension of the inlet valve (9) or outlet valve (8) extends parallel to the axis of rotation (5) of the pump piston (2, 3). Pump according to one of the preceding claims, characterized in that a plurality of outlet valves (8) are arranged close to each other parallel to the axis of rotation (5). Pump according to one of the preceding claims, characterized in that the pump piston (2, 3) has an open projection (40) for triggering the outlet valve (8) in relation to the outlet valve (8). Pump as claimed in any one of the preceding claims, characterized in that the open protrusion projecting towards the end face of the pump piston (2, 3) is in the form of a push rod. Pump as claimed in claim 1, characterized in that the pump (1) has four or two or more pump pistons (2, 3), at least two of which move in a common circular path. Pump as claimed in any one of the preceding claims, characterized in that two pump pistons (2, 3) running in a common circular path are each arranged in separate pump housings (18). Pump according to one of the preceding claims, characterized in that a common drive is provided for the four pump pistons (2, 3) and the drive is arranged in a drive housing (44) separate from the pump housing (18). Pump as claimed in any one of the preceding claims, characterized in that the drive housing (44) is arranged between the pump housings (18). Pump as claimed in any one of the preceding claims, characterized in that, in the case of multiple pump housings (18), the pump housings (18) are configured identically so that they can be exchanged with one another. Pump as claimed in any one of the preceding claims, characterized in that the pump piston (2, 3) or pump housing (18) is coated in the surface area of the movement gap. The pump as claimed in claim 1, wherein the coating is a flocking layer.