JP2918043B2 - Rotary piston machine with stepless flow adjustment - Google Patents

Description

Description: The invention relates to a rotary piston machine according to the preamble of claim 1.

PRIOR ART Known rotary piston machines of the type described above (US-PS413701).
8) has a cylinder structure having a cylindrical inner running surface disposed in a pot-shaped casing,
Since the seal member received on the rotating portion eccentrically supported on the running surface slides along the running surface, the half-moon-shaped working chamber is divided into partial working chambers having a variable volume by the sealing member. You. As a result, a suction period and a compression period occur between the two seal members. The sealing member is received in the rotating part in a vane shape. A control plate is disposed in front of the compression chamber whose volume changes, in the axial direction, and the control plate has a notch around the outer periphery, whereby each of the partial working chambers in the compression period is controlled. The so-called exhaust is kept up to a predetermined rotation angle determined by the rotation of the plate, and the working chamber is kept connected to the return passage for the suction area via a cutout in the control plate.
The return passage is guided axially throughout the cylinder, which receives the rotating part. In this case, the adjustment of the control plate to the desired rotational angle position is performed using a rotating adjustment shaft. The adjusting shaft meshes with the control plate on one side via teeth on the outer circumference of the control plate and is guided axially towards the other side through the entire casing of the compressor with suitable necessary seals. .

The known compressor corresponding to US-PS 4137018 is of the single-flow type, in which the cylinder wall which forms the sickle-shaped working chamber with the rotating part is circular in cross section, so that the non-uniformity of the rotating moment during operation and Pulsation is inevitable. The return flow takes place via a longitudinal passage in the cylinder receiving the rotating part, so that long gas paths and significant flow losses occur.

Furthermore, the notch in the control plate is configured as a surface groove and does not completely penetrate the control plate, forcing the narrow gas to be deflected which causes pressure loss and reduced efficiency when flowing.

A further problem with the known compressors is that the control plate is difficult to move during the adjustment due to the high, uncompensated pressure acting on one side of the control plate, which offers further adjustment possibilities. This inevitably results in leakage between the high and low pressure ranges. That is, the high-pressure gas in the gap between the adjusting shaft and the bore in the stroke ring can flow via the teeth into the cylinder, the overflow passage in the stroke ring, and from there to the suction side. Similarly, pressure in the groove for receiving the seal member in the rotating part may flow out into the overflow passage in the cylinder jacket.

Other rotary piston machines, mainly in the form of vane-type compressors for refrigerants, are known in various configurations (US-PS 3799707, US-PS 4060343, US-PS 3451).
614, US-PS3120814).

In a vane pump, shown in simplified form in US Pat. No. 3,799,707, the control plate is likewise driven by tooth engagement via a knurled nut which drives the pinion externally. In this case, the cutout in the control plate runs completely through it. Of course, in this case, the fluid under high pressure also escapes on the opposite side of the control plate, from which it escapes via the teeth on the outer circumference towards the compressor cover or shaft due to lack of seals. In addition, considerable pressure loss occurs, resulting in lower efficiency.

According to U.S. Pat. No. 4,060,343, the pivoting of the control plate, which is adjusted between the maximum flow and the minimum flow, is by hydraulic means.
This is achieved by dividing the arc-shaped chamber in the casing, which receives and surrounds the control plate, into two pressure chambers. The pressure chamber is loaded with a pressure medium according to the predetermined valve position, so that the control plate is turned.

For automatic pressure adjustment, both sides of the piston member are loaded with the pressure caused by the operation of the refrigerant compressor, and the piston that moves in the axial direction is automatically adjusted via the intermediate gear in the form of a rack. (US-PS 3120814).

The object of the invention is to provide a highly efficient, easily manufactured rotary piston machine in which a light adjustment of the control plate is possible by removing the axial forces acting on the control plate. To provide.

Advantages of the invention The object of the invention is solved by the features of the characterizing part of claim 1, wherein the sealing of the control plate substantially eliminates the pressure acting axially on the control plate, thus providing an adjustment. For this reason, an extremely small adjusting force is required, and on the other side, the advantage is obtained that the fitting error of the control plate can be largely selected in the axial direction and the radial direction based on the seal. In this case, a side seal of the working space is ensured and a precise positioning of the control plate is ensured. This is because friction points on the stroke ring and the seal ring of the control plate are uniquely fixed.

The adjustment of the control plate takes place via a hydraulically / pneumatically double-acting piston / cylinder arrangement, which is controlled by a solenoid valve loaded by control electronics, so that any control The pressure is adjusted.

Advantageous embodiments of the rotary piston machine according to claim 1 are obtained by the measures described below.
Particularly advantageous are extruded gases (or parts thereof)
However, in order to reduce the heating of the compressor, mainly when the discharge rate is adjusted to a minimum, in association with the low rotation speed and the high compression pressure, a suitable cooler such as a refrigerant compressor is collected. In any case, it is supplied to the evaporator of the existing air conditioner, and then cooled and supplied to the compressor again. This significantly reduces the overall temperature of the compressor.

According to another advantageous embodiment of the invention, the control plate is pressed against the stroke ring by an additional pressure plate. In this case, a thrust bearing, for example, a needle ring, can be arranged between the pressure plate and the control plate. This requires a static seal of the pressure plate, the service life of the existing seal ring is longer and the sealing action is improved. On the side of the control plate facing the pressure plate, in practice the friction force no longer acts on the control plate.

According to another embodiment of the invention, the adjusting gear for transmitting the adjusting movement between the pistons is omitted, and the control plate is provided with a toothed neck, which is directly connected to the adjusting machine.

In a further advantageous embodiment of the invention, the ring surface between the control plate and the side plate, in which they are sealed and in contact, is connected to the high pressure side between the sealing rings and the control plate Crimped against the ring.

BRIEF DESCRIPTION OF THE DRAWINGS The invention will now be described with reference to the drawings, in which a rotary piston machine, illustrated as a special embodiment of a vane type compressor 10, comprises a pot-shaped first partial casing 11;
a and a lid-like second partial casing 11b for closing the partial casing 11a. A side plate 12 is fastened between the two partial casings 11a and 11b, and is fixed in this manner. in this case,
The partial casings 11a and 11b are of a suitable type, e.g.
Are connected via a screw connection device indicated by. Within the casing 11 there is a cylinder having an inner running surface 13, which cylinder is hereinafter referred to as a stroke ring 14. The travel ring 14 is connected to the side plate 12 by a suitable screw connection device 15. In this case, a rear closing plate 16 is supported by the screw coupling device, which receives a first rolling bearing 17 for a shaft 19 for driving a rotating part or rotor 18. I have. Since the second rolling bearing 20 is received by the side plate 12, an overall positive centering and a perfect concentric arrangement are provided for the rotating parts and other components. This advantageously acts on the vane or sealing element 22 which is movably mounted in the vane groove 21 in the rotating part, ensuring a light rotation and a perfect fit.

Such a vane type compressor belongs to the related art in various configurations, and is particularly well described from many viewpoints in the publications mentioned at the outset, so that the basic structure and basic function of the compressor will be omitted. I will not explain it.

Therefore, the following description will explain only the differences with respect to the prior art realized by the present invention. In such a vane-type compressor, a well-known control plate 23 which is also known is provided with a side plate.
It is located between the stroke ring 12 and the stroke ring 14 which is open to the left in the drawing plane, so that on the one hand, on the basis of its contour, the respective inlet area 24 is located between the adjacent vanes during operation, It opens to a working chamber of gradually decreasing volume and increasing again, while sealing this working chamber in an increasing compression range.

The latter function of the control plate is variable and relates to the angular or rotational position occupied by the control plate in each case, having a maximum adjustment range of, for example, 90 °. The adjustment range is simultaneously its a stop, defining the maximum flow overdose Q _max and minimum flow overdose Q _min of the fluid being conveyed.

In the illustrated embodiment, the vane-type compressor is of a twin-flow type. In other words, when the rotating part 18 makes one complete revolution, two suction and compression phases are provided between the two vanes 22 per partial working chamber, viewed in the circumferential direction, together with the extrusion phase. For this purpose, the inner running contour 13 of the stroke ring 14 is elliptical in cross section (see FIG. 2). The control plate 23 shown in a simplified plan view in FIG. 3 thus also has two edge cutouts 25a and 25b. The notch 25a
And 25b is consistent with the inflow opening of the inflow range of the control plate 23 and the stroke ring in the starting position for maximum coolant flow overdose Q _max. With the control plate in this position, the compressor operates without adjustment. In this case, the front edge 26 of each notch 25a, 25b when viewed in the direction of rotation determines the amount of intersection between the successive partial working chambers and the suction area 24. Therefore, in the control plate which is a dual-flow type in a dual-flow type refrigerant compressor, the notches which are symmetrically opposed are directed to the suction side. In this case, the control plate is relatively rotated by the notches 25a and 25b, so that a smaller refrigerant flow rate and a smaller refrigerant flow amount in the compressor adjustment range corresponding to the adjustment range shown in FIG. Can be over-adjusted. The basic function of the control plate is, therefore, to define at the leading edge the inflow end, and thus the start of compression, in each partial working chamber that passes. The refrigerant flow overdose by suitably moved in the direction of Q _min is the case can be reduced to about 10% of the maximum amount Q _max. Depending on the position of the control plate, the gas that has been sucked in too much through the respective inlet openings is not compressed and passes through the notch in the control plate and the lateral opening 27 (FIG. 4) provided in the side plate 12. Is returned to the suction range of the compressor. In this case, the working efficiency decreases as the refrigerant transfer amount of the compressor decreases.

Therefore, in the present invention, the notch of the control plate is not only a groove-shaped concave portion but also a complete see-through hole in the control plate material in the outer peripheral region of the control plate. In this case this notch 25
a, 25b, that is, to the right as seen in FIG.
7 is arranged on the side plate 12. The lateral hole 27 has notches 25a, 2
5b is spaced such that it communicates with at least one of the transverse holes 27 independently of the respective position taken in the adjustment range. The amount of gas removed through the lateral holes 27 is returned to the respective suction ranges 24.

By reducing the inflow or lateral opening 27 in the side plate 12 (and the stroke ring 14 connected to the side plate 12 to the right in the plane of FIG. 1), even in the partial load range,
Based on the throttling action, the amount of effective gas sucked in can be changed. The reduction of the inlet opening 27 can be done individually or by providing the notches 25a and 25b of the control plate axially in contact with the inlet opening 27 with a suitable shape.

Thus, in the latter case, the throttle action in the suction range is achieved by the control plate in addition to the pushing action. In this way, the required drive power in the partial load range can be further reduced, since the gas flow does not take place completely without losses.

Another important feature of the present invention relates to the adjustment of the control plate in the angular position occupied by the control plate. That is, for this purpose, at least one piston / cylinder device is provided, which piston / cylinder device is specially supplied for this purpose with a pressure medium or preferably a vane-type refrigerant compressor 10.
In any case (under pressure), the fluid being conveyed acts under the appropriate pressure.

In the first embodiment shown in FIG. 5, a piston / cylinder device 28 is provided, and a predetermined pressure is adjusted on one side of the piston 29 by using a first two-port two-position solenoid valve. On the other hand, for example, suction pressure is supplied to the opposite piston side, that is, the piston side on which the bias or return spring 30 is acting, via a second 2-port 2-position solenoid valve. The piston / cylinder device 28 is provided on the lid-like casing part 11b, as is also well shown in FIG. 1, and below it is also arranged on the casing 11 and preferably on the lid-like casing part 11b. It can be controlled by both two-port two-position solenoid valves 31a and 31b. The piston rod 29a has longitudinal teeth on the side facing upwards in FIG. 5 and meshes with the teeth of the adjusting gear 32. Therefore, the symbol of FIG.
A rack / pinion arrangement is shown, which is often shown at 33. Further, as shown in FIG. 1, the side plate 12 extends to the left in the drawing plane with a hollow boss 12a surrounding the shaft 19, on which an adjusting gear 32 is provided. It is seated with boss-like projections. The projections have teeth on the outer ring surface which are directed over a substantially 90 ° angle to the piston rod or piston shaft depending on the adjustment range of the control plate 23.

To rotate and entrain the control plate 23, the first
In the upper part shown in the figure, the entraining pin 34 extends in the arc-shaped groove 35 in the side plate 12 to the hole 36 of the control plate 23.
Thus, depending on which position the piston 29 occupies in the cylinder 28a of the piston / cylinder device 28, the control plate is given the respective relative angular position. The longitudinal piston movement is transmitted to the control gear by engagement with the teeth of the control gear and from the control gear to the control plate via a driving pin fixed to the control gear. In this case, the adjusting gear 32 is only the arm 32a fixed (integrally) to the adjusting gear,
It extends to the height of engagement with the control plate 23 using the entraining pin 34 (see FIG. 4). Therefore, the inflow opening in the side plate 12
27 is also not covered by the control plate.

Another important feature of the invention is that the control plate 23 is advantageously sealed at the largest possible diameter and with the aid of a closed sealing ring 36.
The advantage of having the sealing member in this position is that the control plate 23 is substantially pressure balanced.
That is, the pressure acting on the control plate 23 in the axial direction is substantially eliminated. In order to allow such a seal with a closed seal ring, the control plate 23 is located on the side facing the side plate 12,
It has a ring projection 37 protruding outward from the ring surface. The ring projections 37 correspond to the corresponding ring notches 38 of the side plate 12.
Engage in. The surfaces provided radially adjacent to one another, i.e. the surface-side ring surface and the outer ring surface, are sealed with a closed sealing ring, for example an O-ring. In this case, at least the outer seal ring 36 must be present.

It is particularly advantageous in this case that the inner radial ring surface 39 is also provided with a separate sealing member 40 in the form of a closed sealing ring, whereby both sealing rings 36 and 40 are arranged. Between the side plate 12 and the bottom of the ring notch 38 of the side plate 12 so as to protrude into the plane of the ring projection 37 or to form a surface 41 adjacent thereto. This space and the space which is created in response to the considerable increase in the radial and axial play of the control plate which is made possible thereby advantageously have a high pressure and a high pressure which is shown in dashed lines in FIG. The load can be applied via the lateral passage 42 to the side. The lateral passage 42 is formed by the entire space inside the larger pot-shaped casing portion 11a and the ring space around the stroke ring 14 connected thereto.

By providing a sealing member in the form of a closed seal ring on the side plate, not only is the pressure acting on both sides of the control plate in the axial direction substantially eliminated, but also by means of said seal the inside of the vane groove 21 Is prevented from escaping to the suction side of the compressor. In this case, the center hole of the control plate 23 and the shaft 19
The space 43 'is intermediate between the high pressure and the suction pressure and under the intermediate pressure acting on the left side of the control plate 23 in FIG. 1 except for the inner ring seal 39. .

If both ring seals 36, 40 are provided and the flat chamber 41 is connected to the high pressure side, this will result in a good seal of the working chamber and thus an improved efficiency of the compressor with less leakage Achieved on the basis of becoming. This is because the control plate is no longer pushed away from the travel ring. This advantage is achieved when the outer diameter of the control plate is chosen to be large, so that the control plate completely covers the stroke cam.

Another advantage of the present invention is that accurate positioning is possible. This is because the friction point of the control plate with respect to the stroke ring and the seal ring is uniquely fixed. This positioning also contributes to the fact that the play in the radial and axial directions of the control plate can be significantly increased.

If the outer seal ring 36 'is arranged further outward as shown in FIG. 11, the inner seal ring can be omitted, but this can of course lead to difficulties in guiding the suction gas.

By means of a sealing element which is arranged as far as possible on the outer periphery of the control plate, at least the intermediate pressure acts on the other side of the control plate outwardly to the extent limited by the seal ring.

According to an advantageous embodiment of the invention shown in FIG. 6, the control plate is adapted to be crimped via a thrust bearing 44 by a pressure plate 43 added to the stroke ring area. Since the functions of the other components are the same as those already described in detail in connection with FIG. 1, the same reference numerals are added to the figures in the drawing of FIG.

In this case, the additional pressure plate 43 is
It engages in a ring notch 45 on the radial surface of a 'with a suitable ring projection 48 which is sealed on both sides by sealing members 46 and 47. The thrust bearing 44 may be a lead ring, and the advantage obtained with this arrangement in addition to the already mentioned pressure offset in the control plate is that it is not necessary to consider only the static sealing of the pressure plate 43. That is. This is because in this case the pressure plate does not rotate with the control plate. The rotational movement is absorbed by the thrust bearing 44. This extends the life of the seal ring and improves the sealing effect. In addition, virtually no more frictional forces occur on the left side of the control plate 23 'shown in FIG. That is, the remaining frictional force is only small on the right side of the control plate.

Another important configuration shown in FIG. 6 is that in this embodiment the front plate or side plate 12 is completely omitted in accordance with FIG. 1, and the control plate is pressed directly into the front lid. That is. In this embodiment, the pressure in the vane groove and the suction pressure are separated by a shaft seal member 49 in the control plate.

A feature of another embodiment of the invention, not shown, is that the pressure connection to the high pressure side, i.e. the connection conduit 42 is optionally closed or opened in accordance with the embodiment of FIG. This is done, for example, with an additional 3-port 2-position directional control valve. Therefore, the control plate 23 is arbitrarily pressed or relaxed. For example, if it is desired to rotate the control plate, the pressing action is reduced. For example, the pressure plate is relieved via a 3-port 2-position directional control valve according to FIG. The existing connection to the high pressure side of the machine is interrupted and the connection to the suction side (or vane groove chamber) is opened. This has the advantage that a larger pressure plate and thus a larger sealing force is possible between the control plate and the stroke ring, in which case the thrust bearing 44 between the pressure plate and the control plate 23 'is omitted. Is obtained. When the control disk rotates, little friction is produced and accurate positioning is possible with little adjustment force.

Further, the adjusting device used to actuate the control plate is shown in FIG. 5 as a single acting piston with a spring return device and controlled via a two-port two-position solenoid valve, This adjustment device can also be implemented in different ways.

FIG. 7 shows a double-acting piston 50 schematically and only on one side. In this case, the right side should be complemented symmetrically. The working chamber on each side of the piston 50 is controlled by a single three-port, two-position directional control valve 51. By using a three-port, two-position directional control valve, both pressure chambers can be evacuated, respectively, so that the adjusted pressure compensation almost avoids the piston from working erratically. The running surface of the piston is formed by a hole 52 in the front closure cover 53. The hole 52 is closed (on both sides) by a plug 54. The piston shaft can act on the control plate directly via the teeth or on the control valve via an adjusting gear.

Further, the double-acting piston shown in FIG. 7 can be controlled by two two-port position control valves. In this case, additionally, this connects both pressure chambers,
Two outlet throttles 55 are provided at the center of the piston. The outlet throttle 55 balances the pressure of each pressure chamber with each other or with respect to the exhaust range.

Another adjustment possibility is shown in FIG. In this case as well, a double-acting piston 56 is provided, which is spring-centered via bias springs 57a, 57b on both sides and has four two-port two-position directional control valves or four. It is controlled via a port 3 position directional control valve. The latter is shown in FIG.

Another possibility of adjusting the control plate (adjustment effect acting directly on the collar projecting from the control plate or via the aforementioned adjustment gear) is shown in FIG. In this embodiment, two step regulators 59a, 59b are provided, preferably in the form of short-stroke cylinders, each controlled by a three-port, two-position directional control valve 60a, 60b. The step adjusters each have one piston-cylinder arrangement and a swivel rod that can pivot on the piston shaft
61a and 61b are arranged. The protruding rods 61a and 61b engage with the driving teeth of the control plate or the adjustment gear and push it. In this case, each of the other protruding rods can escape by being pivotable. The pivotability and workability of each bar is ensured by a spring 62 which contacts the side of this bar.

An embodiment which is advantageous for operation in the present invention has a minimal discharge (in connection with a low rotational speed and a high final compression pressure), and the temperature of the compressor is disadvantageous if gas is forced into the front lids 11b, 11b '. It is based on the fact that it gets too high.

According to one embodiment of the present invention, as shown in FIG. 10, the amount of gas released at the opening 27 (see FIG. 4) is collected and the appropriate cooling via a suitable connecting conduit 63 is performed. The heat is supplied to an evaporator 64 of an air conditioner driven by a compressor, for example, a vane-type refrigerant compressor, and then cooled again via a conduit 65 and returned to the compressor. This makes it possible to reduce the temperature of the vane type refrigerant compressor in a simple manner.

Another feature of another embodiment of the present invention is that the oiling of the solenoid valve and / or the pressure plate is done from the compressor sump instead of the high pressure side sent from the compressor. In this case, the sixth
The supply of high-pressure gas to the pressure plate 43 in the figure is also performed in a flat chamber between the seal members 46 and 47 on both sides, as described using the high-pressure connection conduit 42 as shown in FIG. It is.

The use of a hydraulic pressure medium, ie oil from the sump, results in the shortest dead time during regulation. This is because there is no gas to be compressed or expanded in the adjusting cylinder. Furthermore, there is little leakage at the seal ring of the seal member (piston seal, control plate or pressure plate).

Connect a pressure limiting valve in front of the solenoid valve, and in this case the high pressure reaching 30 bar, which can occur in at most about 10 to
If the pressure is reduced to 15 bar, a commercially available solenoid valve can be used.

A locking member that further engages the teeth of the adjustment gear or control plate,
Providing a spring-loaded member, for example, allows accurate positioning. In this case, fluctuations in the rotational position defined by the piston movement are avoided.

A feature of another embodiment of the piston-cylinder arrangement with a return spring for adjusting the control plate is that the piston-cylinder arrangement has a spring characteristic which is adapted to the overall adjustment characteristic. In this case, a braided spring or a progressively wound spring that avoids the hysteresis phenomenon during the reciprocating motion of the piston can be used.

It is also possible to use gas springs in addition to mechanical springs.

In the embodiment of FIG. 4, it is advantageous to dispose the piston in the opposite direction, that is, to dispose the piston bottom on the right-hand side in the drawing plane. Because the supply amount of refrigerant output is
As the temperature increases, the temperature and thus the pressure in the evaporator decreases. This pressure substantially corresponds to the suction pressure acting on the lower side of the piston and helping to rotate the control plate in the direction of smaller supply. As a result, an automatic adjustment effect that is always effective when the piston diameter is large is exerted.

Furthermore, the respective positions of the control plate, the adjusting gear or the piston are detected by an angle or distance detector (potentiometer, moving coil, short-circuit sensor, etc.), and the obtained signal is supplied to the electronic adjustment device of the refrigerant compressor. Is also advantageous.

The features illustrated in the detailed description, the claims and the drawings of the specification should be regarded as inventions individually or in any combination.

[Brief description of the drawings]

The drawings show a plurality of embodiments of the present invention, and
FIG. 2 is a cross-sectional view of the rotary piston machine shown in FIG. 4, that is, a vane-type compressor, taken along line II. FIG. 2 is a cross-sectional view of a casing of the vane-type compressor having a stroke ring and a rotating part. FIG. 3 is a diagram showing a control plate having a notch in a reduced scale, and FIG. 4 is a diagram showing an adjustment range of the control plate, and FIG.
FIG. 5 is a cross-sectional view taken along the line VV of FIG. 1; FIG. 6 is a cross-sectional view taken along the line VV of FIG. 1; 7 is a cross-sectional view showing a modified embodiment of the vane type compressor shown in FIG. 7, and FIG. 7 is a diagram showing a modified implementation of the adjustment range of the control plate which is adjusted via two pistons loaded on both sides by two 3-port two-way directional control valves. FIG. 8 shows an example, in which the control plate acts directly on the control rod via the protruding rod and the entraining tooth,
FIG. 9 shows an embodiment in which the control plate is adjusted using a short-stroke cylinder controlled by a solenoid valve. FIG. 9 shows an embodiment in which the control plate is adjusted using a spring-centered piston loaded on both sides. FIG. 10 shows an example, FIG. 10 is a schematic perspective view of an embodiment in which the displaced gas or a part thereof is supplied to a cooler (evaporator), and FIG. 11 is a range of a control plate sealing device. FIG. 6 is a diagram showing a modified example of FIG. 11 ... casing, 12 ... side plate, 14 ... stroke ring, 16
... closing plate, 17 ... rolling bearing, 18 ... rotating part, 19 ...
... Shaft, 20 ... Rolling bearing, 21 ... Vane groove, 22 ... Seal member, 23 ... Control plate, 28 ... Piston / cylinder device, 29 ... Piston, 30 ... Return spring, 32 ... Adjustment Gear, 34 ... entrainment pin, 37 ... ring protrusion, 38 ... ring notch, 43 ... pressure plate, 44 ... thrust bearing, 62 ... spring, 64 ... evaporator

Continuing on the front page (72) Inventor Richard Knauf, Federal Republic of Germany Bürertal-Matthausershuitlase 25 (72) Inventor Thomas Mauler, Federal Republic of Germany Flehdatar-Eich Endorfschlasse 47 (56) Reference Document JP-A-61-76793 (JP, A) JP-A-58-72688 (JP, A) Japanese Utility Model Application Sho-63-99005 (JP, U) (58) Fields investigated (Int. Cl. ⁶ , DB name) F04C 29/10 311

Claims (34)

(57) [Claims] 1. A rotary piston machine with a continuously variable flow rate, comprising a cylinder (stroke ring) defining an inner rotational contour and guided along said inner rotational contour arranged in the cylinder. A rotating disk with a sealing member (vane) provided therein and a control disk adjustable in rotational position, the control disk being axially formed and having a compression formed between the vanes. The at least one overflow area (notch) through which the suction gas area is compressed without compressing too much gas in response to the regulated compressor output. The control plate (23,23 ')
A plate (12; cover 11b ') for supporting the control plate (23, 23')
At least one side of the plate (12; cover 11b ')
Are sealed via two sealing members (36; 40),
The adjusting drive for the adjusting movement of the control plate (23, 23 ') is a piston / cylinder device (28), which is loaded with a piston (one side) via a solenoid valve. (29), the pressure adjusted via an electromagnetic valve acts on the upper side of the piston (29), and the suction pressure of the compressor acts on the lower side of the piston together with the return spring (30). It comes into contact with the control plate (23, 23 ') and presses the control plate (23, 23') to the stroke ring (14) and the working chamber which changes the deposition in cooperation with the vane. A rotary piston machine characterized by having a pressure plate (43) that performs. 2. The rotary piston machine according to claim 1, wherein said rotary piston machine is configured as a twin-flow refrigerant compressor having a substantially elliptical inner rotating profile, said control plate being diametrically opposed to said edge-side material cutting. Notch (25a, 25b), and the material notch (2
5a, 25b) controllable control range (Qmax./, Qmin ~ ca.90)
゜) In the side plate (12) or the front casing cover (11
2. The rotary piston machine according to claim 1, wherein the rotary piston machine is aligned at b, 11b ') with laterally spaced apertures (27). 3. The rotary piston machine according to claim 1, wherein the control plate is sealed with a closed sealing ring on a side plate (12) adjacent to the control plate on the side opposite to the stroke ring. 4. The rotary piston machine according to claim 3, wherein the sealing ring is arranged on the outer circumference of the control disk. 5. The method according to claim 1, further comprising the step of providing two sealing rings located on different diameters, wherein a planar chamber is arranged between the sealing rings. A rotary piston machine according to claim 3 or 4. 6. A side plate (12) or a casing cover (11b) adjacent to the control plate (23), the control plate (23) being a ring projection (38) protruding from a radial surface of the control plate (23). The closed sealing rings (O-rings) (36, 40) engaged in the corresponding ring notches
6. The rotary piston machine according to claim 3, 4 or 5, which is arranged on at least one of the two circumferential ring surfaces formed by (8). 7. A closed seal on both opposed circumferential surfaces of the ring projection (38) or the side plate (12) of the control plate (23) or the ring notch (32) of the casing cover (11b). 7. The rotary piston machine according to claim 6, wherein rings (36, 40) are arranged on both sides and the liquid under high pressure is introduced into a chamber on the surface formed between the sealing rings. 8. A connecting conduit (42) is provided from the high pressure side on the other side of the stroke ring (14) to the opposite side (suitably sealed area) of the control plate (23). ,
The rotating piston machine according to claim 7. 9. A two-port two-position directional control valve (31a, 31b) whose outlets are connected to each other, wherein the two-port two-position directional control valve is provided on the upper side (pressure side) of the piston. 9. The rotary piston machine according to claim 8, which supplies a high pressure or a suction pressure generated under control. 10. The rotary piston according to claim 1, wherein the piston / cylinder device (53) has a piston (50) loaded on both sides via two solenoid valves. machine. 11. A three-port, two-position directional control valve (5) for controlling a piston loaded on both sides with high pressure or suction pressure.
11. The rotating piston machine according to claim 10, wherein 1). 12. The rotary piston machine according to claim 10, wherein the pressure chambers on both sides of the piston loaded on both sides are evacuated to one another or to the atmosphere by two outlet throttles (55). 13. A piston / cylinder arrangement having a piston acting on both sides which is centered by spring force via bias springs acting on both sides (57a, 57b), wherein
Both pressure chambers separated by pistons are provided with four 2-port 2-position directional control valves or 4-port 3-position directional control valves (5
2. The rotary piston machine according to claim 1, which is controlled via 8). 14. The piston / cylinder arrangement comprises two step-by-step regulators (59a, 59b) in the form of short stroke cylinders.
The bi-step adjusters (59a, 59b) are controlled by solenoid valves (3 port, 2 position directional control valves 60a, 60b) disposed respectively, and the entrainment teeth that give rotational movement through the attached rods (61a, 61b) are provided. The rotating piston machine according to claim 1, wherein the rotating piston machine is loaded. 15. A tooth is arranged on the shaft of each piston (29, 50, 56) and controls the linear movement of the piston via an intermediate member (adjustment gear 32) or directly on the control plate (23, 23 '). )
Transmitting to give a rotational movement within a predetermined adjustment range,
A rotary piston machine according to any one of the preceding claims. 16. The teeth (33) of the piston shaft (29a) act on the adjusting gear (32) in the form of a rack / pinion connection, the rack / pinion connection entraining the rotational movement produced thereby. 16. The rotary piston machine according to claim 15, wherein the rotary piston machine communicates to the control plate (23) via (34). 17. The entraining pin (34) of the adjusting gear (32).
In the groove (35) cut out in the side plate (12), the control plate (2
17. The rotary piston machine according to claim 16, wherein the rotary piston machine slides radially outward of a sealing area between the 3) and the side plate (12). 18. The rotary piston machine according to claim 16, wherein the side plate (12) forms a boss (12a), on which the adjusting gear (32) is mounted. 19. The rotary piston machine according to claim 16, 17 or 18, wherein the adjusting gear has an arm (32a) for supporting the entraining pin (34). 20. The gas extruded through the notches (25a, 25b) of the control plate collects and is supplied to a cooler (evaporator 64) and then supplied to a suction area of a refrigerant compressor. Item 20. The rotary piston machine according to any one of items 1 to 19. 21. The rotary piston machine according to claim 1, wherein a thrust bearing (needle ring) is arranged between the pressure plate (43) and the control plate (23). 22. The control plate (23 ') is fitted directly into the housing closure cover (11b'), the pressure plate (43) being sealed against the housing cover and under high pressure. 22. The rotary piston machine according to any one of 2 to 21. 23. A control plate for controlling the pressure in the vane groove.
A radial shaft sealing member (49) is arranged to separate against the suction pressure in the above, and the control plate (23 ') is directly in contact with the teeth of the piston shaft when the adjusting gear is omitted with an axial projection. 23. Any one of claims 1 to 22 meshing
The rotary piston machine according to the item. 24. An exhaust device (3 port 2 position valve) for the pressure plate (43) is provided for the high pressure side so as to be connectable to the suction side, thereby eliminating the pressing force applied to the control plate. 24. A rotary piston machine according to any one of the preceding claims, wherein: 25. The rotary piston machine according to claim 24, wherein the control plate (23 ') is in direct contact with the pressure plate (43). 26. A casing of a refrigerant compressor comprising a first bowl-shaped casing part (11a) and a cover casing part (11b) joined to said casing part (11a), and a stroke ring (14) formed by a side plate (11). Abuts on the side plate (12) and is connected to the side plate (12), and is provided with a first
26. The rolling bearing (17) is received in a closing cover (16) in the stroke ring (14) and the second rolling bearing (20) is received in a notch in the side plate (12). A rotary piston machine according to any one of the preceding claims. 27. The rotary piston machine according to claim 1, wherein the housing cover part (11b) receives a piston / cylinder arrangement for adjusting the control plate (23, 23 '). 28. The method according to claim 1, wherein the oil supply to the solenoid valve and / or the pressure plate is effected from a sump of the compressor.
28. A rotary piston machine according to any one of the preceding claims. 29. The rotary piston machine according to claim 1, wherein a pressure control valve is arranged before the solenoid valve. 30. The rotary piston according to claim 1, further comprising a locking member (spring-biased member) for engaging a tooth of the adjusting gear or the control plate. machine. 31. The rotary piston machine according to claim 1, wherein the return spring for the piston / cylinder device for adjusting the control plate has a spring characteristic adapted to the adjusting characteristic. 32. The rotary piston machine according to claim 31, wherein the return spring is wound on a progressive to avoid hysteresis during reciprocation of the piston. 33. The adjusting piston (29), which is biased by a spring on one side, is loaded with suction pressure on the underside of the piston, and the piston diameter increases when the control plate is turned in the direction of decreasing the delivery amount. 2. The rotary piston machine according to claim 1, wherein an automatic adjustment effect that becomes more and more effective is obtained. 34. The respective position of the control disk, the adjusting gear or the piston is determined by an angle or distance measuring device (potentiometer, potentiometer,
34. The rotating piston machine according to any one of the preceding claims, wherein the signal measured and obtained by a moving coil, short circuit sensor or the like) is sent to an electronic conditioning unit for a refrigerant compressor.