JPH02298691A - Control device for rotary piston compressor - Google Patents

Abstract

PURPOSE: To easily set the pressure characteristic, and to reduce the noise by communicating a conduit to be communicated with a pressure chamber with an inlet chamber through a rotary slide valve and a return piping line at the position of the specified rotational angle of the rotary slide valve. CONSTITUTION: A rotary piston compressor is provided with a compressor casing 2 having an inlet chamber 4, an inlet opening 5, a pressure chamber 6 and an outlet opening 7, and an outer rotor 8 is rotatably arranged in the casing 2. The outer rotor 8 is provided with three engagement parts 10, and three working chambers 12 between the engagement parts 10, and an inner rotor 14 having two engagement parts 16 is eccentrically arranged inside. A rotary slide valve 22 having a gap 24 is provided in a casing division 20 to control the communication condition between a conduit 26 to be communicated with the pressure chamber 6 and a return piping 28 to be communicated with the inlet chamber 4 by the rotary slide valve 22. A forward inlet 30 to communicate a valve chamber of the rotary slide valve 22 with the working chamber 12 is formed.

Description

DETAILED DESCRIPTION OF THE INVENTION The invention relates to a control device for a rotary piston compressor based on the features described in the introduction of patent claim 1.

EP-290864^2 discloses such a control device for a rotary piston compressor with an inner sleeve. The rotary piston compressor has an outer rotor within its casing;
Further, an inner rotor having n meshing portions is in cam meshing with the rotor.

The outer rotor has an opening + 1 working chamber, the volume of which is varied corresponding to the rotational angular position of the inner and outer rotors, and the working chamber rotates beside the inlet and outlet openings. It will be done. A rotating piston compressor with an inner ring is
Incorporated for supercharging motor vehicle engines. A valve arrangement is provided between the inlet opening and the outlet opening, which serves on the one hand for partial load regulation and on the other hand for limiting the load pressure in the full load range.

Furthermore, EP 285 tH^2 discloses a rotary piston compressor for supercharging motor vehicle engines, which compressor includes a valve for ventilation regulation in the part load region. The casing has an opening in the area where compression takes place in the working chamber which rotates beside it. This opening is connected to the outlet opening above the valve. When the valve is closed, the maximum possible pressure is generated corresponding to the internal compression. On the other hand, when the valve is opened, the pressure build-up only partially occurs. The valve is either fully closed or fully open, so fine adjustment is not possible. In practice, valves with such valve blades can be disturbed by inserts, in particular interactions with the valve blades that make precise control impossible. Furthermore, vibration generation and blockage due to such valves must be taken into account and additional measures are required.

Furthermore, EP-A 2057750 discloses a control device for a rotary piston device with a control slide valve configured as a rotary slide valve. The rotary slide valve is arranged axially parallel to the axis of the rotary piston device and, corresponding to the respective rotational position of the rotary slide valve, the rotary piston relative to the working chamber of the rotary piston device. This causes a stepless change in the position of the gap around the valve. Corresponding to the rotational position of the rotary slide valve, the volume of the working chamber can be varied in order to enable stepless adjustment of its efficiency.

It is therefore an object of the invention to provide a control device of this kind, in which the pressure characteristics can be set in a simple way and in which a reduction in noise can be obtained, with low manufacturing costs. .

A solution to this purpose is obtained according to the features indicated in patent claim 1.

The control device of the invention is distinguished by its safe-operating construction and allows precise control of rotary piston compressors. Depending on the respective rotational position of the rotary slide valve, the pressure chamber is connected to the working chamber and/or to the inlet chamber. This rotary slide valve makes it possible to precisely control the pressure in the pressure chamber of the compressor on the basis of the respective rotation angle of the valve. First of all, it is important to significantly reduce the noise when installed for supercharging motor vehicle engines, and when the inner and outer compressions are matched and pressure shocks are thus avoided, this It is possible to reduce noise.

Furthermore, when this rotational speed compressor is installed for supercharging a motorized vehicle engine, it is important that the control device requires a small installation space and a small installation weight. The rotary slide valve is rotatably installed in a bore in the casing compartment, and the manufacture of said casing compartment and rotary slide valve can be carried out cost-effectively through mass production.

Advantageously, the casing compartment housing the rotary slide valve is an integral component of the compressor casing. Within the scope of the invention, it is also possible for this casing section to be a separate structural section that is connected to the compressor via a corresponding conduit. Inside the compressor casing there is a front inlet for connection with the working chamber in which pressure is generated.

exists. Through the front inlet and by interaction with the rotary slide valve, a connection can be more or less opened or closed between the working chamber and the pressure chamber. The rotary slide valve causes a change in the cross-sectional area of the connecting part to occur continuously and depending on its position. Furthermore, for the purpose of limiting overpressures, especially during full load operation of engines for motorized vehicles, the rotation is configured such that, depending on the rotational angular position of the valve, the pressure chamber is connected to the inlet output. A slip valve is formed.

In the following, the invention will be explained in more detail using examples of embodiments shown in the accompanying drawings, in which: FIG.

According to FIG. 1, the rotary piston compressor has an inlet chamber 4;
It consists of a compressor casing 2 having an inlet opening 5, a pressure chamber 6 and an inter-outlet lower. Inside the compressor casing 2,
An outer rotor 8 is rotatably arranged around the sleeve perpendicular to the plane of the drawing. The outer rotor 8 includes three meshing parts 10 and three working chambers 12 between said meshing parts. The inner rotor 14 is arranged eccentrically within the outer rotor 8 and is in tooth-lateral contact with the meshing portion 10 on its side surface. The inner rotor 14 has n·2 meshing parts 16 and rotates monotonically with the outer rotor at a rotation ratio of n+1+n. It is obvious that the inner rotor 14 and the corresponding outer rotor 8 can have different numbers of meshing parts. It is advantageous to arrange the inlet chamber 4 and the pressure chamber 6 diametrically opposite each other in the compressor casing 2, as shown, thereby achieving favorable flow conditions with minimal losses and minimal backflow. Ru.

As will be further explained below with reference to FIG.
2 are arranged in a rotatable manner. Furthermore, outside the plane of the drawing, a second gap is provided in the rotary slide valve. This casing section 20 is advantageously an integrated component of the compressor casing 2, but it is also possible for it to be formed as a separate casing part, in which case it will be explained below. A conduit or a corresponding line to the compressor casing 2 is provided. A conduit 26 communicates with the pressure chamber 6 and a return conduit 28 communicates with the inlet chamber 4.

Furthermore, a front inlet 30 is provided within the compressor casing 2. This front inlet 30 is provided between the rear control edge 34 of the inlet chamber 4 and the front control edge 36 of the pressure chamber with respect to the direction of rotation of the outer rotor. In the illustrated rotational position of the rotary slide valve 22, the front inlet 30 is in such a way that the conveyed medium, in particular air, flows through the front inlet and the conduit 26 into the pressure chamber 6 without being compressed. is located. The angular position of the front inlet 30 is such that the angular position of the front inlet 30 is such that in the case of ambient air conditioning in the part load range of the motor vehicle engine as described, no internal compression takes place. Defined based on the geometry of the control edges. Before the second.

The section openings are arranged in a suitable manner in the same way that said front opening 30 is placed in the direction of the long sleeve. Furthermore, a conduit 26 is arranged over the entire width inside the casing 2. In the case of the aforementioned ambient air conditioning, the return line 28 is connected to the rotating bell valve 22.
Closed by.

FIG. 2 shows an axial section through the compressor casing 2,
The outer and inner rotors are not shown here.

The compressor casing 2 is pot-shaped and, after assembly of the rotor, is sealed with a lid attached on the right side in the figure. Eccentrically to the sleeve 38 around which the outer rotor rotates, a hole 42 is provided in the casing floor 40 for the axis of the inner rotor. A pressure chamber 6 opens into the cylindrical inner wall 44 of the compressor casing 2 by means of an outlet lower. Furthermore, the aforementioned conduit 26 leads into the pressure chamber 6 . As previously mentioned, the cylindrical inner wall 44 is connected to the slot 46 of the front inlet 30 described above.
．． 47. The slots 46, 47, like the front inlet 30 integrated into the casing 2 or into the casing section 20, are arranged obliquely and thus correspond to the rotational angular position of the rotary slide valve. , it becomes possible to continuously change the opening cross-sectional area. Slot 46 includes an "upper" end 66. As for the rotary slide valve, only the outwardly extending piston rod 48 is shown here.

FIG. 3 shows an overhead plan view of the compressor casing 2 with a position drive 50 with a control lever 52. FIG.

At the free end of the control lever 52 is a gear rack 54, which meshes with the pinion 5G of the piston rod 48. By means of the position drive 50, the piston rod 48 and the rotary slide valve can therefore be rotated about an axis 58.

FIG. 4 shows an axial cross-section along axis 58 of rotating bell valve 22 within casing compartment 20. FIG. Rotary slide valve 2
2 comprises two gaps 24,25, which work in conjunction with both said front inlet and the conduit. The first gap 24 and the second gap 25 are arranged facing each other at a certain distance in the axial direction, and are otherwise identically formed.

In particular, the rotational angle positions of the rotating bell valve 22 with respect to the pongee 58 are made to match.

Furthermore, the rotary slide valve 22 includes another additional gap 27, which gap is integrated into the return line in the inlet chamber.

The axial length of the additional gap 27 is the same as that of both gaps 24.2.
Advantageously, the axial spacing is less than 5.

A rotary slide valve is rotatably mounted within the casing compartment 20 using roller bearings 60 . A lid 62 is used to seal the hole in the casing compartment 20 that receives the rotary slide valve 22. The gaps 24, 25 and 27 are formed as cut-outs of rectangular cross-section perpendicular to the axis of rotation 5B of the rotary bell valve 22, in which case there is a corresponding linear control edge. Gaps 24, 25 and 27
Advantageously, the bottom surfaces of the two extend as far as the axis of rotation 58 and are arranged parallel to each other. Working in conjunction with the obliquely arranged front inlet, a continuous change in the opening or closing of the cross section results, corresponding to the respective rotational angular position of the rotating bell valve 22. arise. However, within the scope of the invention, the control edges of the gaps 24, 25 and 27 are formed, for example, as curved curves, in order to preserve the desired dependence of the open cross section on the rotational position at each moment. It is also possible. The cross-sectional area opened to the front inlet or both front inlets by the gap 24 , 25 is larger than the corresponding cross-sectional area to the return line 28 opened by the additional gap 27 .

At the same time, it is easily possible for a greater amount of air to be discharged in ventilation operation than in full-load operation, compared to the amount of air that passes back through the return line.

In FIGS. 5 to 7, cutting line A-C according to FIG.
A rotary slide valve in cross-section along is illustrated in various rotational angular positions. In FIG. 5, in contrast to FIG. 1, the rotating belli valve 22 is rotated counterclockwise through a specific angle. The control edge 64 of the gap 24 already partially covers the front inlet 30. Some of the rotating slide valves are as mentioned above.

In addition to the aforementioned gap 24, another second gap 25 is arranged at a distance in the axial direction. The following description of gap 24 applies to the second gap described above. By the dashed line 66,
The upper end or front entrance of the angled slot is shown. The rotary slide valve is used in the above conditions in full load operation for partial internal compression. Corresponding to the position of the rotary slide valve, a pressure equilibrium occurs between the working chamber and the pressure chamber, the compression ratio of which is smaller than the internal compression. Depending on the rotational angular position of the rotary slide valve above the front inlet, rapid pressure equalization processes in the compressor will be avoided in a particularly advantageous manner. Such rapid pressure equalization processes can cause shock generation and significant noise, but these vibrations and noise are significantly reduced by the configuration according to the invention.

Furthermore, the compression work is reduced and the energy balance of the compressor observed over the entire operating range proves advantageous. The position and arrangement of the front inlet and the geometry of the rotary slide valve and in particular of its control edge are given in advance according to the requirements and the necessary adjustment for each engine type. can be done in a reliable manner. It has proven particularly advantageous for the arrangement and configuration to be such that the pressure profile in the working chamber increases monotonically, without any change points due to the rotation of the rotary slide valve 22.

According to FIGS. 6 and 7, the front inlet 30 is completely closed by the rotating bell valve 22. In the position according to FIG. 6, the maximum load pressure for full-load operation is achieved. The compression ratio matches the internal compression of the compressor. Further counterclockwise rotation of the rotary slide valve 22 as shown in FIG. 7 also closes the front inlet 30 as before.

The limitation of the load pressure for full-load operation is illustrated by FIGS. 8 and 9, which correspond to the cross-sectional views along section line AB according to FIG. 2. The aforementioned front inlet is located in front or behind the plane of the drawing, and the veri valve 22 is shown rotating in the area of the cut-out additional gap 27. The rotational angular position in FIG. 8 matches the rotational angular position in FIG. 6, and the rotational angular position in FIG. 9 matches the rotational angular position in FIG. In FIG. 8, the control edge 67 of the additional gap 27 is located just above the conduit 26.
has reached. Further counterclockwise rotation of the rotary slide valve causes the conduit 26 to widen while the return conduit 28
, and the entire cross section of the conduit is then open as shown in FIG. At the same time, an effective and safely operating load pressure limitation is achieved for full load operation of the motor vehicle engine. As seen in connection with FIG. 7, the front inlet remains closed during load pressure limitations in full load operation.

Another operating state is explained with reference to FIG. Compared to the position corresponding to the zero position illustrated in FIG. 1, the rotating valve 22 has been rotated approximately 45° clockwise. conduit 2
6. The front inlet 30 and the return conduit 28 have a gap 24.25.
and through a second gap, which is also not shown in this figure.

The rotating bell valve 22 assumes this position during part load operation when the throttle valve of the motor vehicle engine is closed. Advantageously, during part-load operation, a pressure equilibrium occurs between the pressure chamber and the inlet chamber, so that the compressor works while it is idling and does not have an adverse effect on the closed throttle valve.

FIG. 11 shows one advantageous embodiment of the position drive device 5G, which is here formed as a control container with one membrane 70 and two springs 72, 74. This control vessel includes on the one hand an externally extending control lever 52 with a connection 76 and on the other hand a rack 54 which acts on the pinion 56 and thereby on the rotary slide valve. The connecting portion 76 is connected via a conduit to a tank provided between the throttle lever and the motor vehicle engine. Both springs in the zero state shown? 2.74 is being pulled. In this position, the rotary slide valve assumes the rotational angular position shown in FIG. The increase in pressure on the connection 76 causes the control lever 52 of FIG. 11 to be moved to the left against the force of the spring 72, causing the pinion 56 to rotate counterclockwise, thereby causing the control lever 52 of FIG. A rotary slide valve occupies the rotational angular position shown in the figure. The control vessel includes a pot-shaped membrane dish 78 with an open front face 80 of the membrane dish.
acts as a stopper to limit the maximum movement.

The frontal plane 80 reaches the casing bottom in accordance with the arrow 82, so that the maximum possible movement is achieved and the rotary slide valve reaches the ninth position.
Occupy the position shown in the figure. During part-load operation, the throttle valve is closed, so that a low pressure is applied to the connection 76, which has the effect that the control lever 52 in FIG. 11 is moved to the right. The spring 74 is
It is located inside a pot-shaped portion 84 having a flange 86 . This causes the stop for limiting the maximum movement to move in the negative direction. When the flange 86 is moved fully to the right, as indicated by arrow 88, the maximum extreme position in the negative direction is achieved, and the rotary slide valve assumes the rotational angular position shown in Figure 1 theta. For movement of the position drive within the range indicated by arrow 82, only spring 72 is activated. On the contrary, connection 7
As a result of the low pressure at 6, movement occurs within the range indicated by arrow 88, so that at the same time both springs 72 and 74 are activated. The above-mentioned position drive, which is formed as a control vessel, moves the rotary slide valve in the positive direction indicated by the arrow 82 from part-load operation to full-load operation, including the overpressure limit, with little expense and in a reliable manner. becomes possible. Furthermore, for part-load operation by closing the throttle lever, further negative movements are immediately possible.

FIGS. 12 and 13 show a further embodiment in which the rotary bell valve 22, which is now included in the housing section 22, is integrated directly into the compressor housing 2. FIGS. At the same time, in FIG. 12, the position of the rotary slide valve 22 corresponds to the position according to FIG. 1θ. The pressure chamber 6 is connected to the inlet chamber 4 through a return line 28 .

As can be seen, the working chamber is also connected to the pressure chamber and the inlet chamber. In FIG. L2, one of the positions of the rotating veri valve 22 is indicated by a thin dot-dash line, which position corresponds to the position in FIG.

The rotating bell valve 22 according to this embodiment does not have any straight control edges. On the contrary, as can be seen in FIG. 3, the rotary slide valve 22 is provided in the center with an arcuate gap 90 with a curved control edge 92, which has a straight control edge at both axial ends. Move to the area. It is also possible to provide curved curves or milled surfaces. On the one hand, the return line 28 is closed, and on the other hand, a connection between the front inlet 30 and the pressure chamber 6 is created by means of an arcuate central gap, as shown in dashed lines in FIG. The front inlet is hereby formed by the free area between the device surface 96 of the rotating bell valve 22 on the outer rotor and the outlet control edge 94 of the compressor casing 2.

The description of the control system in connection with a rotary piston compressor having an inner sleeve is not intended to limit the application of the invention to only those types of rotary piston compressors.

On the contrary, the control device with the rotary slide valve of the present invention
Other types of rotary piston compressors can also be used, such as screw compressors and Roots superchargers. Furthermore, for the adjustment of the rotary slide valve, in addition to the above-mentioned position drive with control vessel, electrically controlled servo motors, hydraulic drive controls, etc. are used, in particular. Although the various control functions illustrated in FIGS. 5 to 10 are realized in a particularly advantageous manner using rotary slide valves, it is also possible, on the other hand, to realize only one of these control functions shown. Such embodiments are also included within the scope of the invention.

[Brief explanation of the drawing]

Figure 1 is a cross-sectional view in the radial plane of a rotary piston compressor with an inner sleeve, Figure 2 is a cross-sectional view in the axial plane of the rotary piston compressor along the cutting line A diagram of a rotary piston compressor according to the direction of view of the figures, FIG. 4 is a sectional view taken along section line D-E in FIG. 1, and FIGS. , second
11 is a sectional view of the position drive device, and FIGS. 12 and 13 are 2
2 is a cross-sectional view similar to FIG. 1 of another embodiment of a rotary piston compressor without two rotors; FIG. 2... Compressor casing, 4... Inlet chamber, 6...
Pressure chamber, 8...Outer rotor, lO...Meshing portion, 12...Action chamber, 14...Inner rotor, 20...
・Casing compartment, 22...Rotary slide valve, 24.2
5.27... Gap, 26... Conduit, 28... Return conduit, 30... Front inlet, 34. 36... Control edge, 44... Cylindrical casing inner wall, 46. 47...
・Slot hole, ・50...Position drive device.

Claims (10)

[Claims] (1) A control device for a rotary piston compressor used in particular for supercharging an internal combustion engine, comprising a compressor casing and a pressure chamber, a conduit communicating with the pressure chamber, and the conduit communicating with the pressure chamber. , in particular connected to a return line via a valve arranged in the housing compartment, said return line communicating into the inlet chamber, and further said valve being configured as a rotary slide valve; characterized in that the rotary slide valve has at least one gap, and depending on the rotational angular position of the rotary slide valve, the conduit can be connected to the front inlet and/or the return line via the gap. control device. (2) The control device according to claim 1, wherein the opening cross section can be continuously changed depending on the rotational angular position of the rotary slide valve. (3) in the direction of rotation of the outer rotor of said rotary piston compressor, at least one slot as said front inlet is arranged at an inclined angle in front of the front control edge in the cylindrical inner wall of said compressor casing; 3. The control device according to claim 1, wherein the control device is arranged as follows. (4) The casing section is an integral component of the compressor casing and is located adjacent to and outside the pressure chamber. The control device according to item 1. (5) the compressor casing further comprises one conduit having an axially extending cross section and two axially spaced front inlets, and the rotary slide valve further comprises a conduit having an axially extending cross section; characterized in that it comprises on one part of its outer surface two gaps integrated into said conduit and on the other part of its outer surface one additional gap integrated into said return conduit. The control method according to any one of claims 1 to 4. (6) an additional gap provided for the return conduit,
Control device according to claim 5, characterized in that it has a smaller cross-sectional area than the cross-sectional area of the two gaps provided for connection with the front inlet. (7) the rotary slide valve is rotatable by means of a position drive to which a signal can be sent; the signal corresponds to the pressure in the tank between the throttle lever and the internal combustion engine; 7. The control device according to claim 1, wherein the control device can be switched to another additional signal for controlling the rotational angular position of the valve depending on the pressure. (8) the position drive device is configured as a control vessel, the pressure prevailing after the throttle lever being able to be supplied directly to the control vessel through a connection, and the control vessel being one control vessel; comprising a lever, further characterized in that said control lever starting from a zero position can be moved in one direction by a positive pressure action on the one hand and in the other direction by a negative pressure action on the other hand; The control device according to claim 7. (9) said control vessel comprises a spring in each of the two chambers separated by a membrane, further said two springs are tensioned in the zero position and in full load operation there is a preferential Due to the important adjustment method, only one spring can work, and in part-load operation, both springs can work when low pressure prevails in the chamber with the other spring. The control device according to claim 8, characterized in that it is possible. (10) A position drive device, which is expediently arranged on the compressor casing, acts on the piston rod of the rotary slide valve via a control lever with a rack and a pinion. The control device according to item 8 or 9.