JPH10252602A - Piston pump device for feeding liquid and internal combustion type reciprocating piston engine having the piston pump device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a piston pump device to perform simple control of an amount of feeding liquid and have high efficiency and an internal combustion type reciprocating piston engine having the piston pump device. SOLUTION: A piston pump device 1 to feed liquid, especially fuel, especially heavy oil, is provided with a pump housing 2 having an operation space 3 and a moving piston 4, and the moving piston pump 4 decreases and increases the working space 3. Further, a device 1 is provided with at least one inlet opening 21 to feed liquid into the operation space 3 and an outlet opening 22 to discharge liquid from the operation space 3. A means to control an amount of liquid flowing on the operation space 3 is arranged in the internal space of the pump housing 2. Further, an internal combustion type reciprocating piston engine is provided with a piston pump device 1.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a piston pump device for supplying a liquid, in particular a fuel, in particular a heavy oil, comprising a pump housing having a working space and a movable piston, wherein the movable piston reduces the working space. And an augmenting, and at least one inlet opening for supplying liquid into the working space and an outlet opening for discharging liquid from the working space. Furthermore, the present invention relates to an internal combustion type reciprocating piston engine (Hubkolbenbrennkraftmasch) having the above piston pump device.
ine).

[0002]

2. Description of the Prior Art Generally, a piston pump device operates on the principle that the volume of an operating space in a pump housing changes periodically through reciprocating linear motion of a piston. . The piston is slidable in the front-rear direction while being sealed inside the hollow cylinder. Also, a guide sleeve may be located between the inner wall of the pump housing and the piston. Hereinafter, the movement of the piston that reduces the volume of the operation space is referred to as a compression operation, and the movement of the piston that increases the volume of the operation space is referred to as an expansion operation.

It is known to design compression devices as follows. That is, the piston opens the suction pipe during the expansion operation, thereby allowing the supplied liquid to flow into the working space. During the next compression operation, the piston closes the suction tube, thereby increasing the pressure of the liquid present in the working space. Next, the liquid flows into the pressure line on the high-pressure side through an automatically controlled check valve or the like. The piston
The pump device is used as an injection pump for an injection device of an internal combustion type reciprocating piston engine, particularly a diesel engine. The role of the injection pump is to pump fuel into the injection line at pressures up to about 2000 bar.
In addition, the amount of fuel delivered by the injection pump per operating cycle needs to be controllable between about zero and the full load to achieve the desired output of the machine.

[0004] As a conventional method of controlling the fuel supply amount which is often used, a slope edge control (Schraegkantenr) is used.
egelung). In the inclined edge control, the magnitude of the stroke motion of the piston is generally constant. However, the piston is pivotable about its longitudinal axis. The piston has a groove extending along its outer periphery, the groove communicating with the working space through a flow-off channel. The groove is defined by an edge extending on a peripheral surface of the piston along a direction inclined with respect to the longitudinal axis of the piston. Thus, the distance between the end face of the piston adjacent to the working space and the beginning of the groove is not constant. Thus, based on the angular position of the rotatable piston, the beveled edge opens the inlet opening or special overflow bore earlier or later during the compression operation. As a result, the working space is communicated with the suction side, and the fuel present on the high pressure side in the working space flows to the low pressure side, thereby stopping the fuel supply. Thus, through rotation of the piston about the longitudinal axis of the piston, the distance between the edge of the piston and the beveled edge adjacent to the working space is reduced by the inlet opening or special overflow
Each changes in the bore. When the first mentioned edge closes the inlet opening or a special overflow bore during the compression operation, the fuel supply is started. Further, as the compression operation proceeds further, the fuel supply is terminated immediately after the beveled edge has opened the inlet opening or overflow bore. In this way, the amount of fuel that is effectively supplied can be changed by the flow off of excess fuel on the high pressure side.

[0005] However, piston pump systems of the type described which operate on the principle of inclined edge control have several disadvantages. This control is undesirable in terms of energy, for example, due to the outflow of liquid on the high pressure side. Since a substantially uniform amount of fuel equal to the amount required in full load operation flows into the working space during each operating cycle during the expansion operation of the piston, a relatively large amount of unused fuel is compressed. It is returned from the high pressure side to the suction side during medium, especially at partial load or during idling operation. In this case, the piston must first pressurize any liquid present in the working space,
And this operation requires energy because of the need to create an unwanted liquid return flow for this operation cycle. Since the energy is lost from the actual working process, the energy required for moving and compressing the returned liquid is uneconomical and represents an undesirable loss. This loss has a negative effect on the efficiency of the pump device.
Accordingly, there is a particular need for improvements in applications where the liquid to be supplied is heavy oil used in injection pumps and the like for ship engines.

Furthermore, based on the angular position of the piston with respect to the suction at the opening, ie on whether the pump device is operating in idle mode, partial load mode or full load mode, the piston outer wall And the sealing surface between the guide sleeve and the pump housing is relatively short. This results in a meaningless leak rate that adversely affects the efficiency of the pump.

On the other hand, there is known a piston / pump device in which the amount of liquid to be supplied is controlled through an independent restricting device disposed in front of the pump. In this pump, the piston has substantially smooth walls, and a restrictor located at the front of the pump controls the amount of liquid flowing into the working space in the working cylinder based on the load. However, in this case, the dead volume between the working space of the pump and the restriction device is pressurized during each working cycle, so the dead volume can be problematic. In addition, heavy oil is chemically aggressive and forms very hard deposits, such as in valves of restriction devices. The deposits cause great wear and require high maintenance costs and effort. For this reason, the conventional restriction device is not suitable for supplying heavy oil. Special valves have been developed for heavy oil, but these valves are structurally complex, require high expense, and have relatively high manufacturing costs.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned circumstances, and has as its object to provide an economical piston-pump device capable of easily controlling the amount of liquid to be supplied and having high efficiency. An internal combustion reciprocating piston engine having a pump device. In particular, the piston pump system must be suitable for supplying fuel, especially heavy oil. Piston pump devices need to consume energy more efficiently and have higher efficiencies than conventional devices (eg, devices using inclined edge control).
Furthermore, it is necessary to avoid the formation of dead volumes as much as possible. Piston pump devices need to have a simple and robust design and be economical. In particular, the object of the present invention operates on the diesel principle,
Another object of the present invention is to provide a piston pump device suitable for an injection system of an internal combustion type reciprocating piston engine capable of forming a high pressure required by the diesel principle.

[0009]

SUMMARY OF THE INVENTION A piston pump apparatus according to the present invention includes a pump housing having a working space and a movable piston that reduces and increases the size of the working space. Furthermore, the piston pump device according to the invention has at least one inlet opening for supplying liquid into the working space and an outlet opening for discharging liquid from the working space. The piston pump device according to the invention is characterized by having means in the interior space of the pump housing for controlling the amount of liquid flowing into the working space.

[0010] Since the amount of liquid flowing into the working space can be controlled in the piston pump device according to the invention, the return of liquid from the working space can be avoided. As a result, the supplied energy is used more effectively and the efficiency is improved. Since means for controlling the amount of liquid are provided in the interior space of the pump housing, the formation of undesirable dead volumes can be largely avoided. Further, since no external metering device is required to control the amount of liquid to be supplied, i.e. there is no need to place the metering device ahead of the piston pump device,
Easy and robust economical design is possible. In particular, there is no need to provide a heavy oil resistant external limiting device on the suction side.

A piston according to a preferred embodiment of the present invention
In the pump device, means for controlling the amount of liquid flowing into the working space is provided on the piston. For example, the piston is journalled so that it can rotate about its longitudinal axis. In addition, a control is provided for pivoting the piston about its longitudinal axis. The piston is substantially cylindrical and the means for controlling the amount of liquid flowing into the working space has at least one recess. The recess is provided on the outer peripheral surface of the piston and extends to an end surface of the piston adjacent to the working space.
Based on the angular position of the piston with respect to the pump housing at the end of the expansion operation, i.e., when the piston is at the turning point where the working space has the maximum volume, a smaller or larger opening area of the inlet opening is defined relative to the working space. The recesses are geometrically designed to communicate with each other. Thereby, in this embodiment, the amount of liquid flowing into the working space can be controlled in a simple way, ie by pivoting the piston around its longitudinal axis. Some geometric shapes of the recesses are detailed below.

In order to achieve as symmetrical a pressure distribution as possible, the means for controlling the amount of liquid flowing into the working space preferably have at least two substantially identical recesses on the outer peripheral surface of the piston, and at least two recesses. The two recesses are preferably arranged at diametrically opposite positions and each extend to the end face of the piston adjacent the working space.

In a piston pump device according to another aspect of the present invention, a guide sleeve for guiding a piston is provided in an internal space of the pump housing. The guide sleeve has at least one passage opening through which the liquid to be supplied passes. The position of the guide sleeve with respect to the pump housing can be changed by the control device. In this aspect, the control of the amount of liquid flowing into the working space is performed by pivoting the guide sleeve about the longitudinal axis of the piston, or
This is done by moving the sleeve along the longitudinal axis of the piston. By these means, the position of the passage opening of the guide sleeve can be changed relative to the inlet opening of the pump housing. Thus, when the piston is located at the turning point of the piston which maximizes the volume of the working space, the cross-sectional area through which the liquid flowing into the working space passes also changes. Then, based on the position of the guide sleeve, a smaller or larger area of the inlet opening is closed. Thus, the amount of liquid flowing into the working space can be easily controlled.

The piston pump arrangement according to the invention makes it easy to control the amount of fuel, especially heavy oil, based on load, which makes it particularly suitable for the injection pump of an injection system for an internal combustion reciprocating piston engine. In addition, the high pressures required for diesel engines can be formed. The advantages of the present invention include the improved efficiency of the piston pump device according to the present invention. This is an economical and cost-friendly operation,
And the ability to control the amount of liquid flowing into the working space without the need for heavy oil resistant external limiting devices.

[0015]

BRIEF DESCRIPTION OF THE DRAWINGS In the following detailed description of embodiments with reference to the drawings, a plurality of identical parts or portions having the same functions are denoted by the same reference numerals. As shown in FIG. 1, a piston pump device 1 according to the invention for supplying a liquid, in particular a fuel, in particular a heavy oil, comprises a pump housing 2 having a working space 3 and a movable piston 4.
The movable piston 4 reduces and increases the working space 3, at least one inlet opening 21 for supplying liquid into the working space 3, and an outlet opening 22 for discharging liquid from the working space 3. including. According to the invention, the means for controlling the amount of liquid flowing into the working space 3 comprises a pump
It is provided in the internal space of the housing 2.

A special embodiment of a piston pump device suitable for heavy oil and as an injection pump for a large internal combustion type reciprocating piston engine operating on the diesel principle of a ship engine or the like. The present invention will be described in detail below based on this. Further, the use of the above-described piston pump device in which the liquid to be supplied is heavy oil will be described in detail below. However, the present invention is not limited to these uses. The supply medium may be another fuel or a common liquid. Furthermore, the piston pump device according to the invention is not limited to use in injection systems, but is also suitable for other fields of application in which a controllable amount of liquid is supplied.

The piston pump device according to the invention operates on the conventional principle, that is, the volume of the working space 3 in the pump housing 2 changes periodically through the reciprocating linear movement of the piston 4. Hereinafter, the operation space 3
The movement of the piston 4 that reduces the volume of the operation space 3 is called a compression operation, and the movement of the piston 4 that enlarges the volume of the operation space 3 is called an expansion operation. Furthermore, when the volume of the operating space 3 is maximized, the dead point where the piston 4 is located, that is,
The dead point where the piston 4 is located when the volume of the operation space 3 is minimized, that is, the turning point, is referred to as a second dead point. Therefore, in the example shown in FIG. 1, the compression operation is the rise of the piston 4, the expansion operation is the fall of the piston 4, the first dead center of the piston 4 is the lower dead center, and the second dead center is the lower dead center. Is a dead point located on the upper side.

FIG. 1 is a longitudinal sectional view schematically showing a plurality of components of a piston / pump device 1 according to a first embodiment of the present invention. For clarity of this embodiment, numerous details that are well known in the pump art have been omitted. These details, such as the lines for the blocking oil, inlet and outlet, piston springs, seals and adjusting screws, are similar to designs in commercial injection pumps and the like operating on the principle of inclined edge control. Conventional designs can be used. Therefore,
The description of these details will be omitted.

In the embodiment shown in FIG. 1, the piston 4 is substantially cylindrical and is journalled so as to be able to rotate about its longitudinal axis A. By using a control device having a control rod 6,
The piston 4 is moved around its longitudinal axis A by an arrow C
It can be rotated in both left and right directions as shown by. The control rod 6 has a plurality of teeth on a side surface facing the piston 4, and the plurality of teeth is a tooth arrangement 7 provided on an outer peripheral surface of the piston 4.
Are engaged. Accordingly, in response to moving the control rod 6 leftward and rightward, respectively, as indicated by arrow B, the piston 4 can pivot about its longitudinal axis A in both directions, as indicated by arrow C, respectively. Since the aforementioned control device for rotating the piston 4 is known,
No further detailed description is required. The stroke movement of the piston 4 to reduce and / or increase the working space 3 can likewise take place in a conventional manner. The driven cam shaft 10 rotates, and the rotation causes the cam 11 to move the transmission device 1.
2 is moved upward in FIG. As a result, the piston 4 moves upward in FIG. 1 against the urging force of a piston spring (not shown) and compresses the working space 3. After the cam 11 passes through the transmission device 12, the piston 4 moves downward. Thereby, the operation space 3 is enlarged.

In the first embodiment shown in FIG. 1, the means for controlling the amount of liquid (the amount of heavy oil) flowing into the working space 3 has at least one recess 5, and the recess 5 has a piston 4 And extends to an end surface 49 of the piston 4 adjacent to the operation space 3. To achieve as symmetrical a pressure distribution as possible, preferably at least two
Two recesses 5 are provided on the outer peripheral surface of the piston 4, the at least two recesses 5 being preferably arranged at diametrically opposite positions and each extending to an end face 49 of the piston 4 adjacent to the working space 3. Of course, more than two recesses 5 can be provided, and the same plurality of recesses 5 can be provided.
Are preferably arranged on the outer peripheral surface of the piston 4 so as to be evenly spaced. In this case, that is, when a plurality of recesses 5 are provided on the outer peripheral surface of the piston, more than one inlet opening 2
1 may be provided in the pump housing. It is sufficient to know only one of the plurality of recesses 5 to understand the present invention, and thus only one of the plurality of recesses 5 will be described in detail below.

In the operating state, the recess 5 is used to control the flow of heavy oil into the working space 3. In the example shown in FIG.
The piston 4 is located near the first turning point of the piston 4 (point at which the maximum volume of the operation space 3 is realized). In this state, the recess 5 forms a communicating part between the entrance opening 21 and the working space 3. As indicated by the symbol BE, the heavy oil prepared for combustion reaches the inlet opening 21 through the suction pipe 13 connected to the inlet opening 21, and further from the inlet opening 21 through the recess 5 into the working space 3. Inflow. In a subsequent compression operation, the piston 4 closes the inlet opening 21 and compresses the working space 3. Thereby, the heavy oil in the operation space 3 is pressurized. The pressurized heavy oil flows through the outlet line 22 and the check valve 14 to the pressure line 1.
5 flows into. The pressure line 15 is connected to a pressure container (not shown) connected to the injection nozzle. In the subsequent expanding operation of the piston 4, the space between the inlet opening 21 and the operation space 3 is again communicated via the recess 5. As a result, heavy oil can flow into the working space 3 for the next working cycle. Therefore, the inflow of the heavy oil into the working space occurs during the expanding operation of the piston 4, that is, when the piston 4 is located in the area of the first turning point.

In the piston / pump device according to the present invention, the control of the amount of heavy oil supplied based on the load is performed by controlling the amount of heavy oil flowing into the operation space 3. This control differs from conventional pumps, such as pumps using inclined edge control, in which the amount of heavy oil inflow for each operation cycle is substantially constant and control is realized by a return flow on the high pressure side.

In the embodiment shown in FIG. 1, control of the amount of heavy oil flowing into the working space 3 is performed by rotating the piston 4 about its longitudinal axis A in the direction of arrow C. When the piston 4 is located in the area of its first turning point, a larger or smaller amount of heavy oil flows into the working space 3 based on the angular position of the piston 4 with respect to the pump housing 2. The recess 5 provided on the outer peripheral surface of the piston 4 is geometrically designed. The term "angular position" refers to the rotational position of the piston about the longitudinal axis of the piston, which can be described in an azimuthal angle in a cylindrical coordinate system or the like.

2 (a) to 2 (d) show some examples of the design of the recess 5, each example being shown as a vertical projection on the first projection plane. The first projection surface extends parallel to the longitudinal axis A of the piston 4. The plurality of projections are indicated by reference numerals 51a to 51d. This projection shows a state where the outer peripheral surface of the piston 4 is viewed from a direction orthogonal to the longitudinal axis A of the piston 4. For easier understanding, the longitudinal axis A of the piston 4 is shown in FIGS. 2A to 2D together with the piston 4. Further, the positions of the pump housing 2 and the inlet opening 21 (indicated by broken lines) are shown. FIG. 2A to FIG. 2D show the first turning point, that is,
The piston 4 located near the first dead center (the point at which the maximum volume of the working space 3 is realized) and located at an angular position corresponding to the intermediate amount of the supplied heavy oil, that is, the intermediate amount between the maximum amount and the minimum amount, Show.

The projection 51a shown in FIG.
The recess 5 initially takes the form of a groove 511a extending along an outer circumferential surface extending parallel to the longitudinal axis A from the end face 49 of the piston 4 adjacent to the working space 3 and then changes to a substantially V-shaped portion 512a. The opening side of the V-shaped portion 512a extends substantially parallel to the longitudinal axis A of the piston 4. Therefore, the concave portion 5 contracts along the circumferential direction of the piston 4. That is, the concave portion 5 becomes narrower toward the right side in FIG.

[0026] For example, a higher output is produced using a connected reciprocating piston engine (load increase).
In order to supply a larger amount of heavy oil in each cycle, the piston 4 is turned around the longitudinal axis A to the right in the direction of arrow C1 shown in FIG. 2A using the control rod 6 (see FIG. 1). Move. Thus, when the piston 4 is located in the region of the first dead center, the V-shaped portion 512a opens a larger area of the inlet opening 21. As a result, more heavy oil is
Through the working space 3. Conversely, when reducing the amount of heavy oil supplied per cycle, moving the control rod 6 causes the piston 4 to move around its longitudinal axis A in the direction of arrow C2 (see FIG. 2 (a)). Rotate in the direction. When the piston 4 is located in the region of its first dead center, the area of the inlet opening 21 opened by the recess 5 decreases. As a result, the operation space 3 for each operation cycle
The amount of heavy oil flowing into the interior decreases. When the piston / pump device 1 is set to the maximum supply amount, the broken line indicating the position of the inlet opening 21 with respect to the recess 5 in FIG. When the circle is almost completely arranged in the projection 51a, the concave portion 5 almost completely opens the entrance opening 21. Conversely, if no heavy oil is supplied, for example to stop the connected internal combustion reciprocating piston engine, the piston 4 is moved around its longitudinal axis A by the arrow C2 (see FIG. 2 (a)). , The piston 4 is rotated to an angular position where the broken-line circle indicating the position of the entrance opening 21 with respect to the concave portion 5 is almost completely outside the projection 51a. Therefore, even when the piston 4 is located in the region of the first dead center, the inlet opening 21 is kept closed, and heavy oil cannot flow into the working space 3 at all. By this simple method, that is, by rotating the piston 4, the amount of heavy oil to be supplied can be controlled between the minimum value and the maximum value. Thus, it is an important effect of the present invention that the amount of heavy oil flowing into the operation space 3 can be controlled.

2 (b) to 2 which are similar to FIG. 2 (a).
(D) is a projection 51 b in another example of the recess 5.
To 51d. The operation principle is the same as the operation principle described in detail with reference to FIG. Therefore, the description for FIG. 2A is similarly applied to FIGS. 2B to 2D.

In the examples shown in FIGS. 2B and 2C, respectively, the vertical projection 51b or 51c of the recess 5 on the first projection surface extending parallel to the longitudinal axis A of the piston 4 is substantially Make a triangle. FIG. 2B shows an example in which the projection 51 b of the concave portion 5 forms a triangle, and one side surface of the triangle is located within the end surface 49 of the piston 4. This triangle is in particular a right triangle, the two sides of which are approximately at right angles to each other. Further, on the two side surfaces, the recess 5 has a piston 4
At least one corner position at least respectively extends to a length that almost completely opens the inlet opening 21. In another example of the recess 5 shown in FIG. 2C, the projection 51c is also substantially triangular. However, one side of the triangle is cut by the end face 49 of the piston 4. In at least one angular position of the piston 4, the size of the triangle is set such that the recess 5 opens the inlet opening 21 almost completely.

In another example shown in FIG. 2D, the vertical projection 51d of the recess 5 on the first projection surface extending parallel to the longitudinal axis A of the piston 4.
Is substantially square, especially rectangular. In at least one angular position of the piston 4, the recess 5 has an inlet opening 21.
The size of the square is set so as to almost completely open the box.

Several examples are possible for the formation of the recess 5 in the radial direction, that is, in the direction perpendicular to the longitudinal axis A of the piston 4. FIGS. 3A to 3D show some examples of the shape of the concave portion 5 in the radial direction. And
3A to 3D show the longitudinal axis A of the piston 4.
The vertical projection on the second projection surface extending in parallel to the first projection surface and extending in a direction perpendicular to the first projection surface is shown for various shapes of the concave portion 5. The display as the projection shows a state in which the outer peripheral surface of the piston 4 is viewed from a direction orthogonal to the longitudinal axis A of the piston 4. The direction in which the outer peripheral surface of the piston 4 is viewed is a position rotated by 90 degrees in the circumferential direction around the longitudinal axis A of the piston 4 from the direction in which the outer peripheral surface in FIGS. 2A to 2D is viewed. Reference numerals 52a to 52d indicate vertical projections on the second projection plane, respectively. For the sake of clarity, a part of the piston 4 and the longitudinal axis A of the piston 4 are shown in FIGS.
(D). Furthermore, the pump housing 2 and the inlet opening 21 are shown. FIGS. 3A to 3D show the piston 4 located near the first dead center (the point at which the maximum volume of the working space 3 is realized), respectively.

In FIG. 3A, the projection 52
The shape of the concave portion 5 in the radial direction shown by a is particularly suitable for the concave portion 5 shown in FIG. 2A, but is not limited thereto.
V-shaped portion 512a along the circumferential direction (FIG. 3A)
In the drawing) is tapered along the radial direction. Therefore, the portion 512a looks like a triangle in FIG. The groove 511a connecting the V-shaped portion 512a to the end face 49 of the piston 4 forms a rectangle in the projection 52a.

As shown in FIGS. 3 (b) to 3 (d), the vertical projections 52b to 52d on the second projection surface are substantially rectangular (see the projection 52b in FIG. 3 (b)) and triangular ( The recess 5 may be formed radially to form an at least partially curved area such as a circular segment (see projection 52c in FIG. 3 (c)) (see projection 52d in FIG. 3 (d)).

Furthermore, the radial depth T of the recess 5 (see FIG. 4)
(See (a)), that is, it is possible to form the recess 5 so that the width of the recess 5 along the direction orthogonal to the longitudinal axis A of the piston 4 changes along the circumferential direction of the piston 4. This means that the radial depth T of the recess facing the inlet opening 21 when the oil flows in changes when the piston 4 is rotated about its longitudinal axis A. This is shown in FIGS. 4 (a) to 4 (d).
4A to 4D are plan views of the end face 49 of the piston 4 viewed from the direction of the longitudinal axis A, and show a cross section of the concave portion 5 extending along a direction orthogonal to the longitudinal axis A of the piston 4. Show. The cross sections of the plurality of recesses 5 are indicated by reference numerals 53a to 53d, respectively. Further, it is easy to understand a preferred embodiment of the present invention in which at least two recesses 5 which are provided on the outer peripheral surface of the piston 4 are substantially the same, and the at least two recesses 5 are arranged at positions opposite to each other. For this purpose, two recesses 5 are shown in FIGS. 4 (a) to 4 (d), respectively. 4A and 4B, the recess 5 has a cross section 53a or 53b extending along a direction orthogonal to the longitudinal axis A of the piston 4. The cross section 53a or 53b is practically rectangular, and one side of the rectangular is located on the outer peripheral surface of the piston 4. The rectangular side closer to the longitudinal axis A of the piston 4 can be straight as shown in FIG. 4 (a) or curved as shown in FIG. 4 (b). Thus, at least two side surfaces of the substantially rectangular cross-sectional area 53b are curved. Therefore, the cross-sectional area 53b coincides with the outer periphery of the piston 4, that is, is aligned. Furthermore, as shown in FIG. 4C, the cross-sectional area 53c of the recess 5 extending along the direction perpendicular to the longitudinal axis A of the piston 4 substantially has a boundary line located on the outer peripheral surface of the piston 4. The recess 5 can be formed to have the shape of a circular segment.

FIG. 4D shows another example, and FIG.
It can be used together with the projection 51a shown in (a). The substantially triangular cross-sectional area 53d (shown by a broken line) is shown in FIG.
(D) is located just below the plane of the drawing and the end face 4 of the piston 4
9 through a groove.

The sectional area 5 shown in FIGS.
The point common to 3a to 53d is that the radial depth T of the recess in the region facing the inlet opening 21 changes when the piston 4 is rotated about its longitudinal axis A. . In the cross section shown in FIG. 4B, for example, the radial depth T of the concave portion 5 decreases along the circumferential direction of the piston. The above example of the radial depth T results in that portions of the recess having a greater or lesser depth along the radial direction at least partially open the inlet opening based on the angular position of the piston 4. . By changing the radial depth T of the recess in the circumferential direction in this manner, the amount of heavy oil flowing into the working space 3 is easily controlled by the rotation of the piston 4 about the longitudinal axis A. it can.

There are many possibilities for the three-dimensional shape of the recess 5. For example, these possibilities are illustrated in FIGS.
One of the plurality of projections 51a to 51d on the first projection surface shown in FIG. 2D and the plurality of projections 52a on the second projection surface shown in FIGS. 3A to 3D. To 52d and one of a plurality of cross-sectional areas 53a to 53d shown in FIGS. 4 (a) to 4 (d). Therefore, for example, the amount of heavy oil flowing into the operation space for each operation cycle depends on the geometrical shape of the recess 5 along the circumferential direction of the piston (see FIGS.
(D)) and the change in the radial depth T of the recess 5 (see FIGS. 4 (a) to 4 (d)).
Control alone or through a combination of the aforementioned circumferential geometry and a change in radial depth T.

The corners or edges of the recess 5 shown in FIGS. 2A to 2D, 3A to 3D and 4A to 4D (for example, FIG. 2 (a) V-shaped part 512
a) may be formed slightly round. This can be particularly effective for manufacturing reasons.

In allowing a number of different functional relationships between the rotation of the piston 4 determined by the movement of the control rod 6 (arrow B) and the amount of heavy oil flowing into the working space 3 The numerous possibilities for the shape of the recess 5 described above are particularly advantageous. Therefore, for example, the concave portion 5 can be formed such that the amount of heavy oil flowing into the operation space 3 changes almost linearly with the movement of the control rod 6. For example, recess 5
Has the projections shown in FIGS. 2A and 3A and the cross-sectional area shown in FIG. 4D, the change in the amount of heavy oil flowing into the operation space 3 is caused by the movement of the control rod 6. Depends almost on a quadratic equation. Many such functional relationships can be realized through the geometry of the recess 5. Thus, the piston-pump device according to the invention has the desired control characteristics (the relationship between the movement of the control rod 6 and the change in the amount of liquid).
It has a high degree of flexibility and can be adapted to the requirements of a number of different uses, such as the operation of a generator, a propeller drive or a vehicle drive.

A particular advantage is the high efficiency of the piston pump device according to the invention. Efficiency is the ratio of available output to input. In the piston-pump device according to the invention, only the amount of liquid that actually has to be supplied is respectively supplied into the working space 3. That is, since the amount of liquid flowing into the operation space 3 can be changed, that is, controllable in each operation cycle, the liquid return flow on the high pressure side is unnecessary. This largely avoids moving and / or pressurizing unsupplied liquids. Thus, the energy that needs to be used for such a process can be saved. This increases efficiency and reduces operating costs.

Another advantage of the piston pump device according to the present invention is that the sealing surface between the piston wall and the inlet opening 21 is larger than that of a conventional pump or the like operated using inclined edge control. There is a fact.
This achieves a lower leak rate. This increases efficiency and contributes to efficient use of energy.

When a plurality of recesses 5 are provided on the piston 4, at least one of the plurality of recesses 5 controls one of the pump housings to control the amount of liquid flowing into the working space 3. A piston pump device according to the first embodiment of the invention can be formed to cooperate with over a number of inlet openings 21.

The substantially circular cross section of the illustrated inlet opening 21 is intended to illustrate the present invention and may have other shapes. Therefore, in order to achieve desired control characteristics,
Forming the inlet opening 21 in a slot or elliptical shape may be advantageous.

In the first embodiment, a guide sleeve having at least one passage opening through which the liquid to be supplied can be provided between the outer wall of the piston 4 and the pump housing. Control of the amount of liquid is performed in the same way as in the method described above. For example, when the piston 4 is located in the area of its first dead center, the amount of liquid can be controlled by the recess 5 opening a larger or smaller area of the passage opening.

FIG. 5 is a longitudinal sectional view showing an important part of a piston / pump device according to a second embodiment of the present invention. In the piston pump arrangement, a guide sleeve 8 having at least one passage opening 81 through which the liquid to be supplied passes is provided for guiding the piston 4 to the pump housing 2.
Is provided in the internal space. Further, a control device 9 is provided for changing the position of the guide sleeve 8 with respect to the pump housing 2. As described above in connection with the first embodiment, at least two passage openings 81 are formed in the guide sleeve 8 and the plurality of passage openings 81 are formed.
Is preferably provided on the outer circumference of the guide sleeve 8 at regular intervals in the second embodiment in that a symmetrical pressure distribution is realized. In FIG. 5, a drive mechanism for the compression operation and the expansion operation of the piston 4 is not shown. This can be achieved in a manner similar to the previously known methods. In the second embodiment shown in FIG. 5, the piston 4 has substantially smooth walls and does not rotate around its longitudinal axis A. The amount of heavy oil flowing into the working space 3 is controlled by the guide sleeve 8. The guide sleeve 8 is moved by the control device 9 along the longitudinal axis A of the piston 4 as indicated by the reference symbol D.
For example, this movement can be realized by a transmission rod. Thereby, when the piston 4 is located in the region of its first dead center, the passage opening 81 opens more or less area of the inlet opening 21. FIG. 5 shows the piston 4 located near the first dead center. At the position of the guide sleeve 8 shown, an intermediate amount of oil, ie an intermediate amount between the maximum and the minimum, flows into the working space 3. To increase the amount of liquid flowing into the working space, the guide sleeve 8 is moved upward in FIG. Conversely, if the amount is to be reduced, the guide sleeve is moved downward. When supplying the maximum amount of liquid, the guide sleeve 8 is in a position where the passage opening 81 almost completely opens the inlet opening 21 when the piston 4 is located in the region of its first dead center.
When no liquid is supplied, the guide sleeve 8 is moved downward in FIG. 5 until the guide sleeve 8 almost completely closes the inlet opening 21. Thus, the amount of the liquid flowing into the operation space can be easily controlled.

Another embodiment of the second embodiment comprises a guide sleeve 8 which is immovable in the direction of the longitudinal axis A of the piston 4 while the piston 4
Is rotatable about a longitudinal axis A. Control device 9
Can be formed similarly to the control device for rotating the piston 4 in the first embodiment. In this alternative,
The desired control characteristics can be achieved through the geometry of the passage opening 81. That is, the passage opening 81 can be formed in the same manner as described in relation to the concave portion 5 provided on the outer peripheral surface of the piston 4 in the first embodiment.

Furthermore, in order to control the amount of liquid flowing into the working space 3 through the cooperation of the passage opening 81 and the recess in the guide sleeve 8, the recess is formed on the outer periphery of the piston 4 according to the second embodiment. May be provided on the surface.

The piston pump arrangement according to the invention is particularly suitable for an injection pump of an internal combustion reciprocating piston engine, in particular an injection device of an internal combustion reciprocating piston engine operating on the diesel principle and using heavy oil as fuel. . This type of machine is used for ship engines and the like. About 1000-2000 required for heavy oil on high pressure side
The bar pressure can be established without problems by using the piston pump device according to the invention. Due to its high efficiency, the piston pump device according to the invention allows an efficient use of energy, thereby making a significant contribution to the economical and low-cost operation of an internal combustion reciprocating piston engine.

[0048]

As described in detail above, according to the present invention,
The amount of liquid supplied from the piston / pump device can be easily controlled, and an excellent effect of realizing high efficiency and economy of the piston / pump device is exhibited.

[Brief description of the drawings]

FIG. 1 shows a piston according to a first embodiment of the invention;
FIG. 3 is a longitudinal sectional view showing a main part of the pump device.

FIG. 2A is a partial longitudinal sectional view showing vertical projection of a concave portion on a first projection surface of a piston. (B) Partial longitudinal cross-sectional view showing vertical projection of another concave portion on the first projection surface of the piston. (C) Partial longitudinal sectional view showing the vertical projection of yet another concave portion on the first projection surface of the piston. (D) Partial longitudinal sectional view showing the vertical projection of yet another concave portion on the first projection surface of the piston.

FIG. 3A is a partial longitudinal sectional view showing vertical projection of a concave portion on a second projection surface of a piston. (B) Partial longitudinal cross-sectional view showing vertical projection of another concave portion on the second projection surface of the piston. (C) Partial longitudinal sectional view showing vertical projection of yet another concave portion on the second projection surface of the piston. (D) Partial longitudinal sectional view showing the vertical projection of yet another concave portion on the second projection surface of the piston.

FIG. 4A is a partial plan view showing a cross section of a concave portion located on an end surface of a piston. (B) Partial plan view showing a cross section of another concave portion located on the piston end surface. (C) Partial plan view showing a cross section of still another concave portion located on the piston end face. (D)
FIG. 9 is a partial plan view showing a cross section of still another concave portion located on a piston end surface.

FIG. 5 shows a piston according to a second embodiment of the present invention;
FIG. 3 is a longitudinal sectional view showing a main part of the pump device.

[Explanation of symbols]

1. Piston pump device 2. Pump housing
3 ... working space, 4 ... movable piston, 5 ... recess, 21 ... inlet opening, 22 ... working space, 49 ... end face of piston, 51
a, 51b, 51c, 51d: vertical projection of concave portions on the first projection surface, 52a, 5
2b, 52c, 52d... Vertical projection of the concave portion on the second projection surface, 53a, 53b,
53c, 53d: cross section of a concave portion extending in a direction perpendicular to the longitudinal axis of the piston, 511a: groove, 512a: V-shaped part, A: longitudinal axis of the piston, T: radial depth.

 ──────────────────────────────────────────────────の Continuing on the front page (72) Inventor Robert Hofer Zecher-8353 Elk Schutzenhausstrasse 15

Claims (11)

[Claims] 1. A piston pump device for supplying a liquid, in particular a fuel, in particular a heavy oil, comprising a pump housing (2) having a working space (3) and a movable piston (4); (4) reducing and increasing the working space (3) and displacing the liquid in the working space (3).
At least one inlet opening (21) for feeding into the interior
A piston pump device comprising: an outlet opening (22) for discharging said liquid from the working space (3);
A piston pump device having means for controlling the amount of liquid flowing into said working space (3) in the interior space of the pump housing (2). 2. The piston pump device according to claim 1, wherein a means for controlling the amount of liquid flowing into the working space (3) is provided on the piston (4). 3. The piston (4) is substantially cylindrical and pivotally mounted about its longitudinal axis (A) and is journaled to attach the piston (4) to its longitudinal axis. Means for pivoting around (A), the means for controlling the amount of liquid flowing into said working space (3) having at least one recess (5);
The recess (5) is provided on the outer peripheral surface of the piston (4),
And the end face (49) of the piston adjacent to the working space (3)
3. The piston pump device according to claim 2, wherein the piston pump device extends to at least one of: 4. The vertical projection (51a, 51b, 51) of the recess (5) on a first projection plane extending parallel to the longitudinal axis (A) of the piston (4).
4. The piston pump device according to claim 3, wherein c, 51d) is substantially triangular or square, in particular rectangular. 5. The vertical projection of the recess (5) on a second projection surface extending parallel to the longitudinal axis (A) of the piston (4) and perpendicular to the first projection surface. (52a, 5
5. The piston pump device according to claim 4, wherein 2b, 52c, 52d) is substantially square, triangular or circular. 6. A cross section (53a, 53b, 5) of a recess extending in a direction perpendicular to the longitudinal axis (A) of the piston (4).
The piston and pump device according to any one of claims 3 to 5, wherein 3d) substantially forms a triangle, and a side surface of the triangle is located on an outer peripheral surface of the piston (4). 7. At least two sides of said substantially triangular cross section are curved, said cross sections (53b, 53d).
7. The piston and pump device according to claim 6, wherein the outer diameter of the piston pump corresponds to the outer circumference of the piston. 8. The recess (5) extends from the end face (49) of the piston (4) adjacent to the working space (3) to a groove (511a).
And a substantially V-shaped portion (512)
4. The piston and pump arrangement according to claim 3, which is in communication with a). 9. Piston pump arrangement according to claim 3, wherein the radial depth (T) of the recess (5) decreases along the circumference of the piston (4). 10. The means for controlling the amount of liquid flowing into the working space (3) has at least two substantially identical recesses (5) on the outer peripheral surface of the piston (4), and the at least two recesses (5). 5) Each of the pistons (4) is preferably arranged at diametrically opposite positions and extends to an end face (49) of the piston (4) adjacent to the working space (3).
10. The piston pump device according to any one of claims 9 to 9. 11. An internal combustion reciprocating piston engine having an injection device for injecting fuel, wherein the injection device is at least one piston pump device (1) according to any one of the preceding claims. Internal combustion reciprocating piston engine having