JPH03539Y2 - - Google Patents

Description

[Detailed description of the invention] Industrial field of application The invention relates to a piston pump, in particular a pendulum piston pump, having a pump cylinder and a pump part with a pump head, the pump part being connected to a drive casing. and in which the pump part is fixed to the drive casing in such a way that it forms a gap region and the drive casing interior remains open to the outside via a flow gap.

BACKGROUND OF THE INVENTION In the case of piston pumps, and in particular pendulum piston pumps, a compact design is desired in order to reduce the size of the overall device, that is, the pump part, the drive housing and the electric motor. For this,
It has been proposed that the pump part be flange-connected directly to the drive casing, in particular thereby achieving the desired rigid connection between both parts.

The invention provides that in the case of piston pumps configured in this way, in particular pendulum piston pumps, the heat losses generated in the pump parts are transferred via the pump head and pump cylinder to the drive casing and from there in a dangerous range. It is based on the recognition that it will transition to a crankshaft or pendulum bearing. A particularly disadvantageous situation is that the service life of grease-lubricated ball bearings is impaired.

OBJECT OF THE INVENTION The object of the invention is to eliminate undesirable thermal effects in a simple manner and in a highly reliable way in the area of the drive casing, even in different types of pumps with different crank radii.

Means for Solving the Problems The measures taken to solve the above-mentioned problems are such that the flow gap is provided with a spacer between the pump head and the upper surface of the drive casing on the pump head side. The height of the spacer is adapted to different crank radii or to different piston strokes.

Effect of the invention By opening the gap area, not only a continuous air exchange between the drive casing interior and the surrounding air is achieved during pump operation, but also heat reduction between the pump part and the drive casing. The migration surface is also significantly reduced. In the case of the air exchange described above, the air flowing near the pump section is also used for cooling. Furthermore, configuring the pump in accordance with the invention also serves to control the piston movement associated with volume changes within the drive casing interior.

Furthermore, the pump according to the invention is such that the height of the spacer, that is to say the distance between the pump head and the top of the drive casing, is adapted to the respective crank radius or to the various piston strokes.
If, for example, a pendulum piston pump manufactured in the unit type is intended to shorten the piston stroke by having a smaller structural configuration compared to the basic configuration, this leads to a corresponding shortening of the crank radius. Therefore, it is easily possible. However, without additional configuration, the harmful space is expanded to the region of top dead center. However, such harmful spaces can be reduced in a simple manner by shortening the spacers accordingly. In short, by using such a partition between the pump part and the drive casing with a spacer that easily adapts to the height of their mutual spacing, the piston stroke can be varied by changing the crank radius. At the same time, the size of the hazardous space can be kept constant or to a minimum.

In an advantageous embodiment, the section of the cylinder liner of the pump cylinder extends through the head opening of the drive casing into the drive casing interior, and between the outer contour of the cylinder liner and the inner contour of the head opening. An annular gap is left behind. This not only results in a compact construction, but also allows the air flowing into and out of the housing interior to exert an advantageous cooling effect along the cylinder liner.

Particularly in the case of large pumps, it is advantageous if the blower impeller, which is mounted on the drive shaft, is provided in the interior of the drive housing. This makes it possible to cool the interior of the drive housing and thus the bearings arranged therein in a very simple manner. Particularly when such blower impellers are used, it is advantageous if the suction opening is formed in the drive housing, and preferably the holes are formed in the closing cover of the drive housing.

DESCRIPTION OF THE PREFERRED EMBODIMENTS A pendulum piston pump, designated as a whole by 1, has a pump part 2 and a drive casing 3.
The pump part 2 mainly consists of a pump head 4 and a pump cylinder 5. A connecting rod 7, shown schematically, is guided in the cylinder liner 6 of the pump cylinder. The articulating rod has a sealing piston 8 at its cylinder end and is connected to an eccentric 10 of a crankshaft mechanism 11 by an articulating eye 9 at its drive end. FIG. 2 shows part of the electric motor 12 and its drive shaft 13, which is mounted in a ball bearing 14 on the pump side. In a known manner, the drive shaft non-rotatably supports on the exposed pin 43 the eccentric 10 fixed thereto. The eccentric body 10 is
It is non-rotatably fixed to the pin via a radially arranged retaining screw 15. Furthermore, eccentric body 10
A roller bearing 16 is arranged on the top (second
), this roller bearing is surrounded by an articulating eye 9, which is shown only schematically in FIG. The pump part 2 is fixedly connected to the drive housing 3 via a head screw 17 or a similar fastening element. The fastening element can be, for example, a threaded bolt with an externally arranged fastening nut.

According to the invention, the pump part 2 is not fixed directly, but in the form of a gap region 19, to the drive casing 3, so that the drive casing interior 20 is connected in an open manner with the outer periphery of the pendulum piston pump 1. be done. Therefore, the outside air flows into the drive casing inner chamber 20 from the outside and flows out from the drive casing inner chamber 20 to the outside, as indicated by the double arrow Pf1. In this case, the movement of the articulating rod 7 in the pump cylinder 5 takes into account the change in the volume of the drive housing interior 20, so that the corresponding air movement indicated by the arrow Pf1 already has an additional difference. This is advantageously carried out without any configuration. Such air then moves along the cylinder liner 6 and cools it.

The gap range 19 consists of a radial gap 19a and a lateral gap 19b in the form of an annular gap surrounding the cylinder liner 6 in this embodiment. The transverse gap is formed in the exemplary embodiment in that a section of the cylinder liner 6 of the pump cylinder 5 projects into the head opening 21 of the upper surface 18, in this case an outer contour 22 of the cylinder liner 6. An annular gap or similar radial gap 19a is left between and the inner contour 23 of the head opening 21. Furthermore, as can also be seen in FIG. 1, a spacer, generally designated 24, is provided between the pump head 4 and the upper surface 18 of the drive casing 3 on the pump head side. The spacer is formed, for example, from a tube section 25, as can be seen in FIG. However, the spacer 24 can also be formed by a raised part 26 projecting from the upper side 18 of the drive casing 3 (FIG. 3). Furthermore, as can be seen from FIG.
It can also be formed from a ridge 26 formed on the ridge and a tube section 25' arranged above this ridge. The use of a single penetrating tube section 25 as spacer 24 (FIG. 1) is particularly easy to produce and allows for a height H or It has the advantage of being easily adaptable to h. It is of unit construction and is used in ordinary drive casings.

The embodiment of the drive casing 3 shown in FIG. 3 with a suitably protruding ridge 26 does not require any additional parts and, in some cases, not only the entire upper surface 18 of the drive casing 3. , raised portion 26
It has the advantage that there is no need to process the end face 28 of the. The embodiment according to FIG. 4 combines the aforementioned advantages of the embodiment according to FIG.
The overall height H can be easily adapted to various requirements. Furthermore, as can be seen in FIG. 4, the tube section 25' can also be manufactured from other advantageous heat-resistant materials. As can be seen in FIG. 3, a thin insulating disk 31 can also be provided between the end face 28 of the ridge 26 and the cylinder flange 30 of the pump cylinder 5, so that the tube section 25' By suitably selecting the materials as well, the thermal insulation effect between the pump head 4 and the drive housing 3 can still be increased.

The protruding ridge 26 is always connected to the head screw 17.
or similar, but need not be within the range of
However, it is more advantageous to be located there, which means that the length of the screw guide as well as the transverse gap 1
It is related to the size of the free cross section at 9b. In the embodiment according to FIGS. 1 and 4, the tube sections 25, 25' are advantageously fitted with a threaded head 17.
is arranged around the shaft and is thereby fixed in position without additional construction. In special cases, a ridge similar to that shown in FIGS. 3 and 4 may be added to the cylinder flange 3.
It can also be provided at 0. However, for reasons of fastening technology, it is expedient to arrange such a raised part 26 on the drive housing 3.

In FIG. 1, furthermore, in the cylinder head 4,
A schematically illustrated inlet passage 42, a tension spring-like inlet valve 32, outlet passage sections 33, 34 and suitable valves as outlet valves 35 are shown. In this case, the inlet channel 42 as well as the outlet channel section 33 are shown schematically projecting from the upper side of the pump head 4 for better clarity.

As can be seen in FIGS. 1 and 2, the pump cylinder 5 has at its end adjacent to the pump head 4 a cylinder flange 30 adapted to the end dimensions of this pump head and with a spacer 2.
4 and a threaded head passing through it are arranged in the edge area of the pump head 4. Robustly formed cylinder flange 30 and head screw 17
The above-mentioned arrangement provides a stable, non-tiltable connection between the pump part 2 and the drive casing 3. This means that even if the cylinder liner 6
and the drive casing 3 with a radial gap 1
Even if 9a remains, when operating the pump,
For example, the forces exerted on the cylinder liner 6 can be advantageously transmitted to the drive housing 3.

In FIG. 2, a blower, generally designated 36, is shown located within the drive casing interior 20. The blower 36 consists of a blower impeller 37 mounted on an impeller pin 38 of the drive shaft 13. In the drawing, a number of blades 39 are shown in the area above the blower impeller 37, through which the air loaded flows in the direction of the arrow pf2. In this embodiment, a suction opening 41 for the blower 36 is formed in a thin plate closure cover 40 which closes off the end side of the housing interior 20 of the drive housing 3 . By means of the blower 36 and, if necessary, a suction opening additionally formed therefor, the cooling of the drive housing 3 or the interior of the drive housing can be carried out in a simple manner if required. be strengthened.

As already mentioned, the drive casing interior 20
and the like, because of the thermal transfer of the heat loss occurring in the pump part, only a relatively small thermal transfer cross-section corresponding to the cross-section of the head screw 17 or the like and the cross-section of the spacer 24 is required. This is further aided by the air cooling that is utilized. The outside of the spacer 24 is also cooled by the moved air. In this case, it is advantageous if the spacer has a small cross section. In this case, "small cross section" means
This means that the cross-sectional area of the spacer has approximately twice the cross-sectional area of the associated shaft of the head screw 17. As a result, a sufficient intermediate space is left in the region of the transverse gap 19b even in the region between adjacent heads 17. Furthermore, by suitably selecting the material of the tube section 25', for example if this tube section 25' consists of a material with poor thermal conductivity, the heat transfer can be further reduced. As in FIG. 3, a disk 31 of insulating material can be provided between the pump flange 30 and the spacer 24.

The spacer 24 is installed in order to reduce heat transfer between the pump part 2 and the drive casing 3 and to solve the problem of the invention as explained below: A pump 1 of the type described above is In order to keep production costs as low as possible, they are often constructed and manufactured in unit construction. A number of components, such as drive casing 3, pump head 4, electric motor 12, drive shaft 13, are made of the same material, and as few special components as possible are adapted to the respective efficiency data of the pump required by the customer. . In short, for example, the pump stroke can be varied in a simple manner by attaching articulating eyes 9 with different radii r or R to the drive shaft 13 (FIGS. 1 and 2). However, in the case of conventional types of pumps, it is not possible to start from a basic model with a small "detrimental space" and to modify it to a pump with a large pump stroke. Conversely, it is also not possible to change from a standard-sized pump to a pump with a significantly smaller pump stroke corresponding to a smaller pendulum radius r without significantly enlarging the harmful space. By spatially separating the pump part 2 and the drive casing 3 according to the invention via the spacer 24, the spacing between the pump part 2 and the drive casing 3 can be adjusted very easily when the pump stroke is changed. can be adapted. The harmful space in the region of top dead center can be kept constant, for example as small as possible, in the various strokes. This ensures that the advantageous sealing condition of the pump 1 is maintained by very simple means even when the pump stroke is changed. This represents a particularly advantageous use of spacer 24.

On one side, the drive casing interior 20 and the pump 1
are freely connected by the gap range 19, taking into account changes in the stroke or crank radii r and R, independently of the adaptation of the height h or H of the spacer. On the other hand, if there is no connection between the drive casing interior 20 and the surroundings of the pump, for example the cylinder liner 6 can be connected to the head opening 21.
When mounted in a sealed manner, the height h of the spacer is adapted to suit the appropriate crank radius r; Furthermore, a combination of the above-mentioned height adaptability of the spacer and the ventilation possibility of the interior space is also possible. For example, when enlarging the stroke space in the pump section, the heat loss here becomes comparatively large, so that a suitable cooling of the drive housing interior 20, possibly with the aid of a blower 36, is required. This makes it particularly advantageous.

In the case of the pump 1 according to the invention, not only is the overall construction of the pump device compact due to relatively simple components, but also the heat loss occurring in the pump part 2 can be transferred to the bearings 14, 16 and the pump drive. Keep away from harsh lubricants. Particularly in the case of relatively large pumps 1, forced air cooling is maintained which is further enhanced by the blower 36 and, if appropriate, the suction opening 41 assigned thereto.
This is particularly true if, due to the special position of the pump head 4, the transverse gap 19b has only a small height h. In this case as well, it is advantageous if the pump cylinder 5 or its cylinder liner 6 releases the radial gap 19a and projects into the drive housing 3.

The configurations and embodiments described above can be used individually or in any combination.

[Brief explanation of the drawing]

FIG. 1 is a partially schematic end view of the pendulum piston pump of the present invention, FIG. 2 is a partially cutaway side view of the pump according to FIG. 1, and FIGS. 3 and 4 are views of different implementations. FIG. 3 is a partial cross-sectional view showing an example. DESCRIPTION OF SYMBOLS 1... Pendulum piston pump, 2... Pump part, 3... Drive casing, 4... Pump head, 5... Pump cylinder, 6... Cylinder liner, 7... Connecting rod, 8... Seal piston,
9... Connecting eye, 10... Eccentric body, 11... Crankshaft mechanism, 12... Electric motor, 13... Drive shaft,
14... Ball bearing, 15... Holding screw, 16...
Roller bearing, 17... Screw with head, 18... Top surface, 19... Gap range, 19a... Radial gap, 19b... Lateral gap, 20...
Drive casing inner chamber, 21... Head opening, 22
...outer contour, 23...inner contour, 24...spacer, 25, 25'...tube section, 26...ridge,
28... End face, 30... Cylinder flange, 31
...Insulating disc, 32...Inlet valve, 33, 34...
Outlet passage section, 35... Outlet valve, 36... Blower, 37... Blower impeller, 38... Impeller pin, 39... Vane, 40... Closing cover, 41...
...Suction opening, 42...Inlet passage, 43...Pin.

Claims (1)

[Claims for Utility Model Registration] 1. A piston pump having a pump cylinder and a pump part equipped with a pump head,
The pump part 2 is connected to the drive casing, and the pump part 2 has a gap range 1.
9 and a drive casing inner chamber 20
is fixed to the drive casing 3 in such a way that it remains open to the outside through a flow gap, said flow gap being connected to the pump head 4 and to the upper surface 18 of the drive casing 3 on the side of said pump head. It is formed by providing a spacer 24 between the
Piston pump, characterized in that the height h; H of the spacer 24 is adapted to different crank radii r; R or to different piston strokes. 2. A section of the cylinder liner 6 of the pump cylinder 5 passes through the head opening 21 of the drive casing 3 and projects into the drive casing interior 20, in addition to the outer contour 22 of the cylinder liner 6 and the inner contour 23 of the head opening. The piston pump according to claim 1, wherein annular gaps 19a and 19b are left between the piston pump and the piston pump. 3. The spacer 24 consists of a pipe section 25 and/or a raised part 26 projecting from the upper surface 18 of the drive casing 3 on the side of the pump head 4 towards said pump head.Claim 1. The piston pump described. 4. The pump cylinder 5 has at its end adjacent to the pump head 4 a cylinder flange 30 which at least approximately matches the end dimensions of the pump head and is further provided with a spacer 24, a tube section 25 or a bulge 26 and a head passing therethrough. 4. Piston pump according to claim 1, wherein a screw 17 or a similar fastening element is arranged in the edge area of the pump head. 5. The piston pump according to any one of claims 1 to 4, wherein the blower 36 attached to the drive shaft 13 is disposed in the inner chamber of the drive casing. 6. Piston according to claim 5, in which the drive casing has at least one suction opening 41 for the blower 36, which suction opening is formed in the closing cover 40 of the drive casing 3. pump. 7. Piston pump according to claim 3, in which the tube section 25 or the raised part 26 of the spacer 24 is made of a heat-insulating material and/or the spacers 24-26 are provided with heat-insulating discs 31. 8. Utility model registration requests in which the spacer 24, the tube section 25 or the raised part 26 has a small cross section, which cross section is twice the size of the shaft of the associated headed screw 17. A piston pump according to range 3.