REFRIGERANT COMPRESSOR FOR AIR-CONDITIONING SYSTEMS AND METHOD FOR OPERATING A REFRIGERANT COMPRESSOR

Abstract

A refrigerant compressor for air-conditioning systems and to a method for operating a refrigerant compressor, is based on the object of specifying a solution with which safe functioning of a refrigerant compressor is achieved and in which the effort during production of the refrigerant compressor and the costs are reduced.

Claims

1-9. (canceled)

10. A refrigerant compressor for an air-conditioning system, comprising: a filter arranged in a region in front of a spiral nozzle insert of the refrigerant compressor, as seen in a direction of a mass flow of a refrigerant of the refrigerant compressor, to prevent blockages in the refrigerant compressor, wherein an annular channel surrounding a molding is arranged on a central housing of the refrigerant compressor, that the molding has a circular ring-shaped flat face, and that a friction plate is arranged parallel to the circular ring-shaped flat face, wherein a gap acting as a filter is formed between the circular ring-shaped flat face and the friction plate.

11. The refrigerant compressor according to claim 10, wherein the annular channel is connected via a side chamber to an inflow for the refrigerant of the refrigerant compressor.

12. The refrigerant compressor according to claim 10, wherein a bore, in which the spiral nozzle insert is placed, is arranged inside the molding in the central housing of the refrigerant compressor.

13. The refrigerant compressor according to claim 10, wherein the molding has a trapezoidal or rectangular cross-section.

14. The refrigerant compressor according to claim 10, wherein a size of the gap is within a range between 0.1 mm and 0.2 mm.

15. The refrigerant compressor according to claim 10, wherein an inner diameter of the circular ring-shaped flat face of the molding is within a range between 6 mm and 12 mm, and that a width of the circular ring-shaped flat face of the molding is within a range between 1 mm and 3 mm.

16. A method for operating a refrigerant compressor, in which particles exceeding a predefined size are filtered out in a region in front of a spiral nozzle insert of the refrigerant compressor, as seen in a direction of a mass flow of a refrigerant of the refrigerant compressor, wherein an annular channel surrounding a molding is provided in a central housing of the refrigerant compressor, that the molding is provided with a circular ring-shaped flat face, and that a friction plate is provided parallel to the circular ring-shaped flat face, as a result of which a filter which retains the particles exceeding the predefined size is formed by a gap between the circular ring-shaped flat face and the friction plate.

17. The method according to claim 16, wherein the mass flow of the refrigerant takes place via a side chamber with an inflow into the annular channel via the gap into the spiral nozzle insert provided in a bore, wherein the particles exceeding the predefined size are retained by the gap and thus do not reach the region of the spiral nozzle insert.

18. The method according to claim 16, wherein the gap is provided with a size between 0.1 mm and 0.2 mm.

Description

BRIEF DESCRIPTION OF DRAWINGS

[0030] Further details, features and advantages of embodiments of the invention can be found in the description of exemplary embodiments below with reference to the associated drawings. In the drawings:

[0031] FIG. 1: shows a detail of a region of a refrigerant compressor in which the gap or gap filter is formed, in a sectional diagram,

[0032] FIG. 2: shows a detail of the region of the refrigerant compressor in which the gap or gap filter is formed in a view from above of the molding for forming the gap,

[0033] FIG. 3: shows a sectional diagram of the bore for the spiral nozzle insert of the refrigerant compressor with the gap or gap filter formed on the inlet side,

[0034] FIG. 4: shows an exemplary dimensioning of the gap or gap filter and of the bore for the spiral nozzle insert of the refrigerant compressor, and

[0035] FIG. 5: shows a graph showing the mass flow of a refrigerant through the gap or gap filter as a function of a gap blockage.

DESCRIPTION OF AN EMBODIMENT

[0036] FIG. 1 shows a detail of a region of a refrigerant compressor (1) in which the gap (11) or gap filter is formed, in a sectional diagram.

[0037] FIG. 1 shows a refrigerant compressor (1) with a part of its central housing (2). In the central housing (2), a cylindrical bore (3) has been introduced, in which a spiral nozzle insert (4) with its coils (5) has been introduced. The central housing (2) has an annular channel (6) which runs in a circle around the bore (3) and is connected to an inflow (7) (not shown in FIG. 1 for a refrigerant.

[0038] In the central housing (2), between the annular channel (6) and the bore (3) for the spiral nozzle insert (4), a molding (8) is formed surrounding the bore (3), said molding having a trapezoidal or rectangular cross-section. This region of the molding (8) in the central housing (2) is shown in FIG. 1 by means of a dotted line.

[0039] The gap (11) or gap filter according to the invention is formed between a circular ring-shaped face (9) of the molding (8) and a friction plate (10) closing the refrigerant compressor (1). To this end, the trapezoidal or rectangular molding (8) in the central housing (2) is designed such that there is a spacing, which is within a range between 0.04 and 0.16 mm, between the circular ring-shaped face (9) of the molding (8) and the friction plate (10).

[0040] The refrigerant passing via the inflow (7) into the annular channel (6) moves through the gap (11) and passes into the bore (3) to the spiral nozzle insert (4). This mass flow (12) of the refrigerant is shown in FIG. 1 by means of multiple arrows.

[0041] Owing to the provided dimensioning of the gap (11) formed according to the invention, particles exceeding a predefined size are filtered out in that these particles cannot pass via the gap (11) into the region of the spiral nozzle insert (4).

[0042] Such particles are thus prevented from blocking the region of the spiral nozzle insert (4) with its nozzle, as is achieved according to the prior art by the use of a separate small-meshed filter.

[0043] FIG. 2 shows a detail of the region of the refrigerant compressor (1) in which the gap (11) (cf. FIG. 1) or gap filter is formed. FIG. 2 shows a view from above of the molding (8), which is elevated in a ring shape, for forming the gap (11) with the friction plate (10) removed.

[0044] FIG. 2 shows the central housing (2) with the introduced cylindrical bore (3), in which the spiral nozzle insert (4) with its coils (5) is arranged.

[0045] Also shown is the annular channel (6) which runs in a circle around the bore (3) and is connected at least indirectly to the inflow (7) for a refrigerant.

[0046] It is provided for there to be produced in the annular channel (6) a peripheral mass flow (12) of the inflowing refrigerant which is as uniform as possible and thus a uniform flow around the annular channel (6) and the molding (8) on all sides. To this end, the inflowing refrigerant is introduced via an inflow (7) first into a side chamber (14) partially flow-connected to the annular channel (6). From this side chamber (14), the refrigerant then flows via a transition region (15) into the annular channel (6). Such a transition region (15), which extends for example over a circular segment section of the annular channel (6) within a range between 60 degrees and 100 degrees, allows an improved, uniform introduction of the refrigerant over a larger area into the annular channel (6), in comparison with a direct supply of the refrigerant into the annular channel (6) via the inflow (7). The transition region (15) is indicated in FIG. 2 by means of a dashed line.

[0047] Owing to the indirect introduction of the refrigerant into the annular channel (6) via the side chamber (14) and the correspondingly sized transition region (15), turbulence in the mass flow (12) of the refrigerant, as occurs at small openings and/or at edges, is reduced.

[0048] In the view from above of FIG. 2, the circular face (9) for forming the gap (11) is also shown. This circular face (9) is part of the molding (8) in the central housing (2) of the refrigerant compressor (1).

[0049] Multiple arrows show the mass flow (12) of the refrigerant from the inflow (7) via the annular channel (6) and many points of the annular gap (11) to the spiral nozzle insert (4) with its coils (5).

[0050] FIG. 3 shows a sectional diagram of the bore (3) in the central housing (2) for the spiral nozzle insert (4) of the refrigerant compressor (1) with the gap (11) or gap filter formed on the inlet side.

[0051] On the inlet side means that the gap (11) is formed in a region in which the mass flow (12) of the refrigerant reaches the inlet region of the spiral nozzle insert (4) from the annular channel (6) via the gap (11).

[0052] FIG. 3 also shows the friction plate (10) attached to the central housing (2) of the refrigerant compressor (1). It can be seen that the gap (11) is formed between this friction plate (10) and the molding (8) of the central housing (2).

[0053] FIG. 3 also shows the side chamber (14) connected to the annular channel (6) and the inflow (7) via which the refrigerant flows into the annular channel (6). In the region of the inflow (7), the letters BP stand for a back pressure.

[0054] The refrigerant filtered via the gap (11) or gap filter flows through the coils (5) of the spiral nozzle insert (4) and passes to a nozzle-like end (13) shown at the lower end of the spiral nozzle insert (4) in FIG. 3. In this region too, the mass flow (12) is shown by way of example by means of two arrows. In the region of the nozzle-like end (13), the letters LP stand for a low pressure.

[0055] As is usual in the prior art, the spiral nozzle insert (4) can have a countersunk bore in the region of its central axis, as shown by way of example in FIG. 3.

[0056] FIG. 4 shows a detail of the central housing (2) of the refrigerant compressor (1) in the region of the gap (11) or gap filter and the bore (3) for the spiral nozzle insert (4) with an exemplary dimensioning.

[0057] The mass flow (12) of the refrigerant of the refrigerant compressor (1) is also shown in FIG. 4 by means of multiple arrows. The refrigerant flows via the inflow (7) and the side chamber (14) into the annular channel (6). In the example of FIG. 4, this annular channel (6) has an inner diameter of 11 mm and a channel width of 2.3 mm, the channel width having a greater value in the region of the inflow (7). The height of the ring-shaped annular channel (6) is indicated to be 1 mm by way of example.

[0058] From this annular channel (6), the refrigerant flows via the likewise annular gap (11) to the spiral nozzle insert (4) with its coils (5). In the example, the gap (11) forming between the molding (8) and the friction plate (10) has a width of 0.15 mm. In FIG. 4, the trapezoidal molding (8) of the central housing (2) is indicated by way of example by means of a dotted line.

[0059] In the example of FIG. 4, the spiral nozzle insert (4) with its coils (5) has been introduced into a bore (3) with a diameter of 8 mm and has the countersunk bore already known from FIG. 3.

[0060] FIG. 5 shows a graph showing the mass flow (12) of a refrigerant through the gap (11) or gap filter as a function of a gap blockage.

[0061] In the graph of FIG. 5, a gap blockage R.sub.s in % (per cent) is shown on the abscissa or x axis. A gap blockage means the accumulation of particles at the gap (11), which cannot pass through the gap (11) owing to their dimensions. These accumulations correspond to the filtered particles retained by a filter designed according to the prior art.

[0062] In the graph of FIG. 5, a mass flow or volumetric flow q.sub.m of the refrigerant flowing through the gap (11) in kg/h (kilograms per hour) is shown on the ordinate or y axis.

[0063] The graph of FIG. 5 shows the curve of the mass flow or volumetric flow q.sub.m of the refrigerant as a function of the gap blockage R.sub.s.

[0064] As has been found, an accumulation of particles exceeding a predefined size at the gap (11) has no or only an insignificant effect as long as this gap blockage R.sub.s remains below a rate or a value of 90%.

[0065] The volumetric flow q.sub.m of the refrigerant, which is approximately 1.91 kg/h in the example of FIG. 5, thus remains virtually constant in the range of a gap blockage R.sub.s of 0% to 90%. Functional operation of the electrical refrigerant compressor (1) and prevention of blockages by particles exceeding a predefined size are thus ensured within this range.

[0066] Only upwards of a gap blockage R.sub.s of more than 90% does a decrease in the volumetric flow q.sub.m of the refrigerant occur, which can have a negative effect on the operation of the electrical refrigerant compressor (1). In the case of a gap blockage R.sub.s of approximately 95%, the volumetric flow q.sub.m of the refrigerant is thus reduced to a value of approximately 1.85 kg/h, which corresponds to a reduction in the volumetric flow q.sub.m of the refrigerant of approximately 3%. In the case of a gap blockage R.sub.s of approximately 98%, the volumetric flow q.sub.m of the refrigerant is reduced to a value of approximately 1.6 kg/h, which corresponds to a reduction in the volumetric flow q.sub.m of the refrigerant of approximately 16%.

[0067] The diagram shows that the safe operation or functional safety of the gap filter according to the invention formed by the gap (11) is ensured over a very wide range of a gap blockage R.sub.s.

LIST OF REFERENCE NUMERALS

[0068] 1 Refrigerant compressor [0069] 2 Central housing [0070] 3 Bore [0071] 4 Spiral nozzle insert [0072] 5 Coils [0073] 6 Annular channel [0074] 7 Inflow [0075] 8 molding [0076] 9 Circular ring-shaped face [0077] 10 Friction plate [0078] 11 Gap [0079] 12 Mass flow [0080] 13 Nozzle-like end [0081] 14 Side chamber [0082] 15 Transition region