EP2828528A1

EP2828528A1 - Refrigerant compressor

Info

Publication number: EP2828528A1
Application number: EP13711632.3A
Authority: EP
Inventors: Dominic Kienzle; Ashraf AGHA; Stephan Rölke
Original assignee: Bitzer Kuehlmaschinenbau GmbH and Co KG
Current assignee: Bitzer Kuehlmaschinenbau GmbH and Co KG
Priority date: 2012-03-20
Filing date: 2013-03-19
Publication date: 2015-01-28
Anticipated expiration: 2033-03-19
Also published as: RU2589978C2; US20150004015A1; DE102012102349A1; WO2013139772A1; RU2014141936A; US10648472B2; EP2828528B1; CN104204532A; CN104204532B

Abstract

The invention relates to a refrigerant compressor comprising a common housing; a screw compressor that is provided in the common housing, said screw compressor comprising a compressor housing, which is formed as a part of the common housing and which is equipped with at least one screw rotor bore, comprising at least one screw rotor arranged in the screw rotor bore in a rotatable manner about a rotational axis, comprising a suction-side bearing unit arranged on the compressor housing for the screw rotor, comprising at least one pressure-side bearing unit arranged on the compressor housing for the screw rotor, and comprising a housing window provided on the compressor housing for compressed refrigerant; and a first muffler unit arranged in the common housing. The aim of the invention is to further improve the refrigerant compressor with respect to the sound-damping capability. This is achieved in that the first muffler unit is arranged adjacently to the housing window, and the muffler unit has at least one chamber which lies between an inlet opening and an outlet opening and which expands transversely to a flow direction relative to the inlet opening and to the outlet opening.

Description

REFRIGERANT COMPRESSOR

The invention relates to a refrigerant compressor, comprising an overall housing, a screw compressor provided in the overall housing with a compressor housing formed as part of the overall housing, in which at least one screw driver bore is arranged, with at least one screw rotor rotating in the screw driver bore about an axis of rotation, with one on the Compressor housing arranged on the suction side bearing unit for the screw rotor, with at least one arranged on the compressor housing pressure side bearing unit for the screw rotor and with a provided on the compressor housing housing window for compressed refrigerant and arranged in the overall housing first muffler unit.

Such refrigerant compressors are known from the prior art, for example DE 103 59 032 A1.

The invention is therefore based on the object to further improve a refrigerant compressor of the generic type with respect to the sound attenuation.

This object is achieved in a refrigerant compressor of the above

described type in that the first muffler unit is arranged in the pressure housing following the housing window, and that the muffler unit has at least one lying between an inlet opening and an outlet opening, transverse to a flow direction relative to the inlet opening and the outlet opening widening chamber. The advantage of the solution according to the invention can be seen in the fact that the fact that the silencer unit is provided immediately following the housing window, the pressure pulsations in the refrigerant compressor can not spread over long distances, but again immediately after their formation within the compressor housing at the outlet window the muffler unit are damped.

In particular, this opens up the possibility that the pressure pulsations do not propagate over a significant part of the refrigerant compressor, but are attenuated substantially immediately after their formation in the region of the outlet window and the passage through the housing window, so that the spread in the overall housing of the refrigerant compressor of sound is largely reduced.

With regard to the specific arrangement of the silencer unit so far no further details have been made.

Thus, an advantageous solution provides that the first silencer unit is arranged in a silencer housing adjoining the compressor housing in the region of the housing window.

Such a silencer housing can be formed and held in various ways. So could be a gap between the housing window and the muffler housing.

An advantageous solution provides that the muffler housing the

Housing window tightly overlaps and thus the silencer housing itself receives the compressed and pressure pulsations having refrigerant directly on the housing window and tightly rests around the housing window around. It is particularly expedient if the muffler housing itself forms the inlet opening, the outlet opening and the at least one chamber, that is to say that no additional insert parts are required in the muffler housing, but the muffler housing forms the inlet opening, the outlet opening and the at least one chamber as a unitary component ,

Furthermore, it is preferably provided with respect to the silencer housing that the silencer housing is arranged next to a bearing housing accommodating at least one pressure-side bearing unit, that is, that the bearing housing for the at least one pressure-side bearing unit seen in the direction of the axes of rotation of the screw rotor, and the silencer housing not consecutive, but lying side by side and thus are arranged side by side in a direction transverse to the axes of rotation.

With regard to the fixation of the silencer housing so far no further details have been made.

In principle, the muffler housing could be fixed to the pressure housing.

It is particularly favorable, however, if the muffler housing is held on the compressor housing, whereby in particular a seal of the muffler housing around the housing window around is easy to implement.

Since usually also the bearing housing is held on the compressor housing, both the muffler housing and the bearing housing are preferably held adjacent to the compressor housing.

In order to arrange the muffler housing and the bearing housing in a simple manner next to each other, provides a particularly favorable solution that the muffler housing and the bearing housing as parts of a combined housing are formed, that is, by the

combined housing both the bearing housing for the bearing units and the muffler housing for the at least one muffler unit is realized.

On the one hand, this enables a cost-effective production of the combined housing and, on the other hand, also simplifies the assembly of the bearing housing and the muffler housing, in particular if both of these are held on the compressor housing.

With regard to the design of the combined housing a variety of solutions are conceivable.

For example, it is possible to produce the combined housing in one piece.

For reasons of simplified manufacturability of the combined housing, however, it is advantageous if the combined housing is designed in several parts.

For example, it is provided that the combined housing comprises a base housing and a cover, so that thereby simplify the manufacture and assembly of the combined housing.

With regard to the subdivision of the combined housing in the base housing and the cover housing are the most diverse possibilities of

Separation of the same conceivable.

An advantageous solution provides that the base housing and the cover housing are separable by a transverse to the axis of rotation of the at least one screw rotor separating plane. Such a course of the parting plane makes it possible to form and mount the base housing and the cover housing in a particularly simple manner.

In particular, it is advantageous to mount the base housing to the compressor housing and to mount the cover housing seated on the base housing and to fix it to the base housing.

For example, it is provided in such a construction that in the base housing at least a part of the bearing housing and at least a part of the muffler housing is formed.

It is conceivable, for example, that at least part of the chambers of the silencer unit is formed in the base housing.

It is even more advantageous, if also in the base housing between the chambers lying partitions are formed.

With such a solution, the silencer unit according to the invention can be realized very simply and inexpensively.

In particular, it is preferably provided that the base housing is an integral part.

For example, the base part can be formed as a casting, in which the chambers and the partitions and the respective part of the bearing housing are formed, so that so that the base housing together with the respective part of the muffler unit and the cover is very easy to produce.

In addition, it is also advantageous if the cover housing is an integral part. In the cover, for example, the second silencer unit is formed. In particular, the cover housing is made as a casting, in which, for example, the corresponding part of the bearing housing and also the corresponding part of the silencer unit is formed.

With regard to the further construction of the silencer unit, provision is preferably made for the first silencer unit to have a receiving chamber adjoining the outlet window, to which the inlet opening follows, so that the first silencer unit can be adapted to the outlet window in a simple manner, the receiving chamber compacting the same Receives gas or refrigerant from the outlet window and the inlet opening of the first silencer unit supplies, so that the receiving chamber provides in particular for an adaptation of the cross sections of the outlet window to the cross section of the inlet opening.

A particularly advantageous arrangement of the first muffler unit according to the invention provides that it is arranged so that the compressed refrigerant can flow in a flow direction which is transverse to a pressure side wall of the compressor housing and away, in particular approximately parallel to a rotation axis of the at least a screw rotor, that is in a direction which forms an angle of at most 30 ° with the axis of rotation runs.

In this way, the first muffler unit according to the invention can be arranged in a particularly space-saving manner.

Furthermore, preferably, the first muffler unit extends in the direction parallel to the rotational axes of the screw rotor over approximately the same distance as the bearing housing in order to achieve a space-saving solution.

In an advantageous solution, it is provided that the muffler unit is formed as a passage damper, which at least one through hole and at least one on this passage opening having the following expansion chamber and wherein the inlet opening and the outlet opening also each form a passage opening for the at least one expansion chamber.

This means that in this case, the muffler unit thereby their

Damping function achieved that cross-section jumps between the through holes and the expansion chambers and between the expansion chambers and the through-holes occur, the extent of

Damping is dependent on the area ratio of the cross-sectional jumps.

Preferably, it is provided in such a silencer unit that it has a plurality of passage openings on which one each soft

Expansion chamber follows.

In particular, in this case, the muffler unit is designed so that immediately following each expansion opening an expansion chamber, and preferably also so that immediately after each expansion chamber, a through hole follows.

In the simplest case, in particular in the realization of the silencer unit in the combined housing, the silencer unit can be designed such that each through opening opening into an expansion chamber passes without supernatant into a chamber wall of the respective expansion chamber, so that the expansion chamber and the through openings can be easily, that is in particular without undercuts as a one-piece part, in particular as a casting, produce.

Moreover, it is also preferably provided for the same reasons that in each expansion chamber, a chamber wall passes without supernatant into the passage opening leading away from the expansion chamber. The silencer unit according to the invention is particularly easy to produce if several of the through-openings of the silencer unit have identical cross-sections.

It is particularly favorable if all passage openings of the silencer unit have identical cross sections.

In particular, it is advantageous if the passage openings are aligned with each other.

Furthermore, it is preferably provided that the silencer unit has a plurality of expansion chambers with different volumes, so that it is thus possible in a simple manner to tune the damping properties to different frequencies.

The different volume of the plurality of expansion chambers can be achieved particularly advantageously in that the expansion chambers with different volumes have a different expansion in the

Have flow direction.

As an alternative or in addition to the previous solutions relating to a passage damper, a further advantageous solution provides that the silencer unit comprises a pipe section which extends from the inlet opening to the outlet opening and forms a throughflow channel which has shell-side openings which are arranged in at least one in the at least one chamber and to the pipe section

lead to adjacent damping chamber.

In this case, the muffler unit no longer works as a passage damper but as a branch resonator or Helmholtz resonator, in which the damping chamber across the openings to the flow channel across the Coupled flow direction and thus dampens the pressure pulsations in the flow channel in the case of a defined by the apertures and the damping chamber resonance condition.

Preferably, it is provided that the pipe section passes through a plurality of chambers, each of which adjacent to the pipe section

Damping room forms.

In this case, there is a resonance condition for each of the damping chambers together with the openings leading to them.

In this case, the damping chambers are at several Dämpfungsräumen

separated from each other.

For example, it is provided that the muffler unit has at least two damping chambers, which have a different volume.

In particular, the different volume of the damping chambers can be realized in that they have a different extent in the longitudinal direction of the pipe section.

In connection with the previous explanation of the individual embodiments of the solution according to the invention was not defined in more detail how the silencer unit should be arranged in the overall housing.

For example, it would be conceivable to design the overall housing in such a way that it forms the muffler housing with one part.

In the case that the muffler housing and the bearing housing are combined to form a combined housing, it is also conceivable to form the overall housing so that a part thereof forms the combined housing. However, a further advantageous solution provides that the muffler housing is disposed within a pressure housing of the overall housing, that is, that within the pressure housing still the muffler housing is formed as a separate housing.

This can be achieved, for example, by the fact that the pressure housing engages over the muffler housing and thus the possibility is created of further reducing the sound propagation starting from the muffler housing in the direction of the pressure housing.

In particular, it is expedient here if the muffler housing is surrounded by a pressure chamber located in the pressure chamber, wherein the pressure chamber ensures that a sound attenuation occurs between the muffler housing and the pressure housing.

In particular, the pressure chamber is a space in which the compressed gas or refrigerant enters only after passing through the muffler unit and thus the muffler housing, so that in the pressure chamber, the pressure pulsations of the compressed gas or refrigerant are already damped by the muffler unit.

In addition, a further advantageous solution provides that in the pressure housing, a Schmiermittelabscheideeinheit is arranged.

Thus, a lubricant separation can be combined with a sound attenuation in a simple manner.

Preferably, the Schmiermittelabscheideeinheit is arranged so that it is arranged downstream of the at least one silencer unit, so that the compressed gas or refrigerant on reaching the Schmiermittelabscheideeinheit no longer has pressure pulsations, which is advantageous for a lubricant separation, since pressure pulsations in the Schmiermittelabscheideeinheit cause already deposited lubricant is again entrained by the compressed gas or refrigerant due to the pressure surges.

Further features and advantages of the inventive solution are the subject of the following description and the drawings of some embodiments.

In the drawing show:

Fig. 1 is a perspective view of a refrigerant compressor according to the invention;

Fig. FIG. 2 is a side view in the direction of the arrow A in FIG. 1; FIG. Fig. 3 is a view in the direction of arrow B in Fig. 1; Fig. 4 is a view in the direction of arrow C in Fig. 1 Fig. 5 is a section along line 5-5 in FIG. 4

Fig. 6 is a perspective view of an end-side cover with

a bearing seat facing the cover from the engine compartment side;

7 is a perspective view of the lid of FIG. 6 with a view of a suction gas connection on the lid;

Fig. 8 shows an enlarged section through the frontal cover with the

Suction gas connection and the bearing receiver;

9 is a section along line 9-9 in FIG. 5; 10 is a section along line 10-10 in FIG. 5;

11 is a section along line 11-11 in FIG. 4;

Fig. 12 is an enlarged section similar to FIG. 11 in the region of a pressure housing;

13 is a view similar to FIG. 12 of a second embodiment of a refrigerant compressor according to the invention;

14 shows an illustration similar to FIG. 12 of a third exemplary embodiment of a refrigerant compressor according to the invention;

FIG. 15 is a view similar to FIG. 12 of a fourth embodiment of a refrigerant compressor according to the invention;

FIG. 16 is a view similar to FIG. 12 of a fifth embodiment of a refrigerant compressor according to the invention; FIG.

17 is a view similar to FIG. 12 of a sixth embodiment of a refrigerant compressor according to the invention and

18 is a view similar to FIG. 12 of a seventh embodiment of a refrigerant compressor according to the invention.

An in Fig. 1 to 3 illustrated embodiment of a refrigerant compressor according to the invention has an overall housing 10, which is a Ver ^¬ denser housing 12, a on one side of the compressor housing 12 ange ^¬ arranged motor housing 14 and on a motor housing 14 against ^¬ opposite side of the compressor housing 12 arranged pressure housing 16th includes. In this case, the compressor housing 12, the motor housing 14 and the pressure housing 16 separate parts of the overall housing 10 and the Forming the same be composed of it or the compressor housing 12 and the motor housing 14 and / or the compressor housing 12 and the pressure housing 16 may be formed as a continuous parts.

Furthermore, the motor housing 14 contributes in the region of a partial circumference

Control housing 18, in which a controller for the refrigerant compressor is arranged.

As shown in Fig. 2, 3 and 5, the motor housing 14 encloses an engine compartment 20 and is closed at its end facing away from the compressor housing 12 by an end wall of the motor housing 14 forming frontal cover 22, which in turn is provided with a suction gas connection 24 via which can be supplied to the refrigerant compressor to be sucked refrigerant.

As shown in FIG. 2 and 3, the suction gas connection 24 is preferably provided with a shut-off valve 26, which is connected to a suction gas line leading to the refrigerant compressor, not shown in the drawings.

In this case, the shut-off valve 26, as shown in FIG. 3, about an axis 28 in different rotational positions, for example, in four mutually rotated by 90 ° rotational positions, mountable to allow optimal adaptation to a leading to the refrigerant compressor, not graphically illustrated suction gas line.

The possible in different rotational positions mountability of the shut-off valve 26 can be realized that at equal angular intervals about the axis 28 arranged retaining screws 32a, 32b, 32c and 32d are arranged, with which the shut-off valve 26 in the four rotated by 90 ° rotational positions relative to the lid 22 is mountable. The pressure housing 16 is detachably connected to the compressor housing 12, via a pressure housing flange 34 which is connectable to a mounting flange 36 of the compressor housing 12, starting from the pressure housing flange 34, the pressure housing 16 in the form of a cylindrical, end closed by an end wall 48 Capsule 38 extends.

Furthermore, the pressure housing 16 carries a compressed gas connection 42, to which a pressure-gas-side shut-off valve 44 can be mounted.

Preferably, the capsule 38 is also still accessible in the area of its end wall 48 opposite the compressor housing 12 with an access cover 46 accessible (FIGS. 1 and 4).

As shown in Fig. 5, sitting in the motor housing 14 a designated as a whole by 50 electric motor, a fixedly disposed in the motor housing 14 stator 52 and a relative to the stator 52 about a motor shaft 54 rotatably mounted rotor 56, the rotor 56 on a Drive shaft 58 is seated.

On the one hand, the drive shaft 58 passes through the rotor 56 in the direction of the motor shaft 54 and on the other hand extends into the compressor housing 12 of a screw compressor designated as a whole by 60.

In its extending in the compressor housing 12 area carries the

Drive shaft 58 a screw rotor 62 which is disposed in the compressor housing 12 in a helical bore 64 and in this about a coincident with the motor shaft 54 axis of rotation 63 is rotatable.

In addition, the drive shaft 58 extends on its opposite side of the electric motor 50 on the screw rotor 62 and forms an end portion 66 which is rotatably mounted in a disposed within the pressure housing 16 bearing housing 68, for this purpose in the bearing housing 68, a pressure-side bearing set 72nd is provided. Further, the drive shaft 58 between the screw rotor 62 and the rotor 56 in a to a suction side of the screw rotor 62nd

then arranged suction side bearing set 74 stored.

For example, the suction side bearing set 74 is held on a suction side wall 76 of the compressor housing 12, while the pressure side bearing set 72 is held on a pressure side wall 78, for which purpose the bearing housing 68 is supported by the pressure side wall 78.

For exact guidance of the rotor 56 coaxial with the motor shaft 54, the drive shaft 58 still has a beyond the rotor 56 also extending end portion 82, which in turn is mounted in a guide bearing 84 which sits in a coaxial with the motor shaft 54 arranged bearing receptacle 86, the fixed is arranged on the motor housing 14, close to the lid 22nd

In this case, the bearing receiver 86 could be supported directly independent of the cover 22 on the motor housing 14.

Preferably, the Lageraufname 86, as shown in FIG. 5, Fig. 6 and Fig. 7, held on the cover 22, wherein the bearing receptacle 86 is held by a plurality of webs, for example, the equiangularly spaced webs 88a, 88b or 88c, at a distance from a lid bottom 92.

In particular, the bearing receptacle 86 comprises a receiving bottom 85, which is supported by the webs 88a, 88b and 88c, and an annular body 87, which encloses the guide bearing 84 radially outboard.

In the lid bottom 92, a suction opening 94 is also provided, to which the suction gas connection 24 connects and thereby aligned with this. By the webs 88a, 88b, 88c, the bearing receptacle 86 is held at such a distance from the lid bottom 92 that forms between lid bottom 92 and bearing receptacle 86 in the direction of the motor shaft 54 and the motor axis 54 extending inflow space of itself between the in Surrounding direction successive webs 88 extending inflow openings 96a, 96b and 96c is surrounded, through which the suction gas with respect to the motor axis 54 axial and radial component, as shown in FIG. 8 shown by dashed lines, can enter into an end-side interior 100 of the engine compartment 20.

Preferably, a suction gas filter 98 is arranged around the bearing receptacle 86 in the interior 100, through which the suction gas has to flow.

The suction gas flows, as shown in FIG. 5 and 8 shown in dashed lines, from the shut-off valve 26 in the direction parallel to the motor shaft 54 through the suction gas connection 24 and the suction port 94 into the inflow space 90, which is arranged between the suction port 94 and the bearing receptacle 86.

From the inflow space 90, the suction gas then flows with a component running obliquely to the motor axis 54 through the inflow openings 96 into the interior 100, forming a plurality of flow paths S.

In this case, for example, a first flow path S1 flows through the bearing receptacle 86 in the region of the outer annular body 87, which surrounds the guide bearing 84 radially outwardly and preferably flows around the annular body 87, so that the bearing receptacle is cooled.

Furthermore, this flow path S1 also flows to the rotor 56 at its end face 104 facing away from the compressor housing.

Furthermore, for example, a flow path S2 flows to the stator 52 in the region of its winding heads 102 facing away from the compressor housing 12 in order to cool them. A further flow path S3, for example, opens up the possibility of flowing through a gap 108 between the rotor 56 and the stator 52 in the direction of the compressor housing 12, thereby also providing both cooling of the stator 52 and cooling of the rotor 56.

In addition, for example, forms a flow path S4, and through this is as shown in FIG. 9, the stator 52 flows around in the region of radially outwardly extending recesses 106 in the direction of the compressor housing 12 and thereby cooled radially outboard.

The intake opening 94 in the cover 22 is preferably arranged such that the motor shaft 54 passes through it, in particular the intake opening 94 is arranged coaxially to the motor shaft 54, so that approximately rotationally symmetrical flow conditions arise in the region of the inner space 100 and the bearing receptacle 86 relative to the motor axis 54.

The guide of the suction gas to form the flow paths S takes place on the one hand by the receiving base 85 and the annular body 87 of the bearing receptacle 86, which form the Sauggasstrom Strömungsführungsfiächen 89, as well as by Strömungsführungsfiächen 99, which are formed after the suction port 94 in the lid bottom 90 and expand progressively from the intake opening 94 with increasing extent in the direction of the compressor housing 12.

After flowing through the recesses 106 and the gap 108, the suction gas collects in the region of the compressor housing 12 facing

Winding heads 112 of the stator 52 in a compressor housing-side interior 116 of the motor housing 14 and is capable of this, too

Winding heads 112 to cool before the sucked gas or refrigerant, as shown in FIG. 10, passes through apertures 114a, 114b and 114c provided in the suction-side wall 76 of the compressor housing 12, thereby entering a suction chamber 118 of the compressor housing 12. As shown in FIG. 10 and Fig. 11, in addition to the first screw rotor 62 is still a second, cooperating with this and in one

Screw rotor bore 120 arranged screw rotor 122 is provided, wherein the second screw rotor 122 is mounted about a parallel to the motor axis 54 and the rotation axis 63 axis of rotation 123 by means of a end over the screw rotor 122 projecting bearing shaft 124 in a pressure-side bearing set 126 and a suction-side bearing set 128 is stored.

The two screw rotors 62 and 122 now work together in such a way that refrigerant or gas is sucked in from the suction space 118, compressed by the intermeshing screw rotors 62 and 122 and defined as compressed gas or refrigerant in the region of a pressure-side outlet window 132, by the peripheral regions and end side regions free on the pressure side the screw rotor 62, 122 exits into the compressor housing 12, and from the compressor housing 12 passes through a housing window 133 in the pressure housing 16.

For adjusting the volume ratio, a slider 134 is furthermore provided for this purpose, the design and function of which is described, for example, in German Patent Application 10 2011 051 730.8.

In order to dampen the pressure pulsations of the compressed gas or refrigerant exiting through the outlet window 132, a first silencer unit 140 is provided immediately after the housing window 133 in the pressure housing 16, which housing chamber 138 adjoins the housing window 133, one on the housing window 133 opposite side of the receiving chamber 138 arranged inlet port 142 and an outlet port 144, which in a transverse to the pressure side wall 78 and directed away therefrom, in particular to the motor axis 54 parallel flow direction 146 are flowed through, between the inlet port 142 and the outlet port 144, for example a plurality of chambers 148a and 148b, 150a, 150b and 150c, which widen transversely to the flow direction 146, are provided and each of the chambers 148 and 150 is, as shown in FIG. 12, separated by a dividing wall 152 from the closest chamber 148, 150, each dividing wall 152 having a flow restricting passage 154 through which the compressed gas or refrigerant may pass from one of the chambers 148, 150 to the other.

In particular, the passage openings 154 are each designed so that their extension in the

Flow direction 146 of the thickness of the partition wall 152 corresponds, so that the passage openings pass without walls in wall surfaces of the partition wall 152.

In the same way, the inlet opening 142 and the outlet opening 144 also pass over into the wall surface of the adjoining chamber 148 or 150 without any projections.

Preferably, the chambers 148, 150 have different chamber volumes.

Such different chamber volumes can be achieved, for example, in that the chambers 148, 150 have the same dimensions transversely to the flow direction 146 or radially to the latter, but have different dimensions in the direction of the flow direction 146.

In the embodiment of FIGS. 11 and 12, the inlet port 142, the through holes 154, and the outlet port 144 are coaxial with a central axis 156, and likewise the chambers 148 and 150 are coaxial with the central axis 156, such that the first muffler unit 140 to the central axis 156 is rotationally symmetrical. In particular, the central axis 156 extends parallel to the axes of rotation 63 and 123 of the screw rotors 62 and 122 and thus parallel to the motor axis 54.

For example, the chambers have 148 and 150 is an inner diameter D _ik of more than 1.3 times, more preferably more than 1.4 times an inner ^¬ diameter Did of the through holes 154 and the inlet port 142 and outlet port 144th

In addition, an extension A _K i ₄ 8 of the individual chambers 148 is more than about 0.2 times, more preferably more than about 0.23 times the inside diameter D _{ik of} the chambers 148, 150.

At most, the extent of the chambers 148, 150 in the direction of the central axis 156 corresponds to the inner diameter D _{ik of} the chambers 148, 150, even better is a maximum value of D _{ik of} the half of the inner diameter D _{ik of} the chambers 148.

In contrast, the extension A _k i _{50 of} the chambers 150 is more than about 0.1 times the inner diameter D _{ik of} the chambers 150.

Subsequent to the first muffler unit 140, for example, there is still a second muffler unit 160, which has a transverse flow chamber 162 adjoining the outlet opening 144, through which the compressed gas or refrigerant exiting the first muffler unit 140 moves in a direction of flow 164 transverse to the flow direction 146 in the direction of an outlet 166 of the second silencer unit 160, from which then the compressed gas or refrigerant in a channel 168, for example, formed by a tube 172 to the end wall 48 of the capsule 38 is guided and there radially through openings 174 in the tube 172nd exits and enters a tube 172 enclosing the pressure chamber 176 of the pressure housing 16. Around the channel 168, in particular around the tube 172, a Schmiermittelabscheideeinheit 180 is disposed in the pressure chamber 176 of the pressure housing, which, for example, two sets of porous gas permeable

Structures 182 and 184, for example of metal, which provide for deposition of lubricant mist from the pressurized gas or refrigerant.

After flowing through the Schmiermittelabscheideeinheit 180 then the pressurized gas or refrigerant has the ability to exit via the compressed gas connection 42 from the pressure housing 16.

The lubricant that collects in the lubricant separation unit 180 forms a downstream portion of the pressure housing 16 and the compressor housing 12 a lubricant bath 190 from which lubricant is received, filtered by a filter 192, and used for lubrication.

In connection with the previous description of the first muffler unit 140 and the second muffler unit 160, nothing was said about their arrangement.

Preferably, both the first muffler unit 140 and the second muffler unit 160 are arranged in a muffler housing 200, which is integrated, for example, in the bearing housing 68 or molded onto it, so that the bearing housing 68 and the muffler housing 200 together form a combined housing 210 which within the pressure housing 16 is arranged and in turn is supported by the pressure-side wall 78 of the compressor housing 12.

The combined housing 210 can be constructed on the one hand to form the bearing housing 68 and on the other hand to form the muffler housing 200 in a variety of ways. Preferably, the combined housing 210 is constructed in two parts and includes a base housing 212 which is connected to the pressure side wall 78 of the compressor housing 12 and which receives the pressure side bearing sets 70 and 126 and also a portion of the chambers 148 and 150, for example the chambers 148 and a Part of the chambers 150.

A cover housing 214, which receives the transverse flow chamber 162 and a part of the chambers 150 and forms a cover for the pressure-side bearing sets 72 and 126, is then seated on the base housing 212 fixedly connected thereto.

Starting from the cover housing 214, the tube 172 then extends in the direction of the end wall 48.

In particular, the base housing 212 and the cover housing 214 are separable by a geometric separation plane 216 which extends transversely, preferably perpendicular to the axes of rotation 63, 123 of the screw rotor 62, 122.

The combined housing 210 can be advantageously produced as a casting, in which the muffler units 140, 160 and the bearing housing 68 are formed near the final contour near the mold.

A lubrication of the guide bearing 84 and possibly the bearing sets 72 and 74 and 126 and 128 via central lubricant channels 222 and 224 of the drive shaft 58 and the bearing shaft 124, the guide bearing 84 and possibly the bearing sets 72 and 74, 126 and 128 for lubrication Supply oil.

In one embodiment of a refrigerant compressor according to the invention, shown in Fig. 13, the combined housing 210 'is formed so that the parting plane 216' between the base housing 212 'and the Cover housing 214 'runs at such a distance from the compressor housing 12, that all chambers 148 and 150 of the first muffler unit 140 are located in the base housing 212 and also the outlet opening 144 in the base housing 212' is located, so that in the cover housing 214 'nor the Querströmkammer 162 of the muffler unit 160 is disposed and the outlet 166 of the second muffler unit 160th

Thus, the part of the bearing housing 68 which is arranged in the base housing 212 ', such an extent that the bearing sets 72 and 126 are arranged in this and the Abdeckgehäuseteil 214' only one cover of the bearing housing 68 includes, which the rest, in the Base housing 212 'arranged part of the bearing housing 68 covers.

Incidentally, the second embodiment is formed in the same manner as the first embodiment, so that the contents of the statements relating to this in connection with the first embodiment can be made and identical reference numerals are used for identical parts.

In a third embodiment of a refrigerant compressor according to the invention, shown in FIG. 14, the combined housing 210 "is again configured differently, such that the base housing 212" has a minimal extent starting from the compressor housing 12 and thus comprises only the receiving chamber 138 with respect to the first muffler unit 140, while already the inlet opening 142 and thus Also, the chambers 148 and 150 in the cover housing 214 "are arranged, and also the cover housing 214" also the entire second muffler unit 160, in particular with the cross-flow chamber 162 and the outlet 166, receives. However, this is also due to the position of the parting plane 216 "a substantial part of the bearing housing 68 is not disposed in the base housing 212", but in the cover 214, arranged "so that a substantial part of the bearing sets 72 and 126 in the cover 214" and not in the Base housing 212 ".

Incidentally, the third embodiment with respect to the other features is identical to the preceding embodiments, so that with respect to these features in full reference can be made to the comments on the above embodiments, wherein identical parts are also provided with identical reference numerals.

In the first to third embodiments, the muffler units 140 and 160 are formed as so-called passage damper, that is, between the inlet port 142 and the outlet port 144 at least one chamber, for example, the chambers 148 and 150 are located, which in turn are separated by passage openings 154 from each other such that the compressed gas or compressed refrigerant undergoes multiple flow constriction and subsequent expansion as it flows through the muffler units 140 and 160.

In contrast, in the following fourth to seventh embodiments, instead of the first muffler unit 140, a first muffler unit 240 is provided which, although also in a direction parallel to the axes of rotation 63 and 123 of the screw rotor 62 and 122 flow direction 146 can flow, but operates on a different principle ,

In such a muffler unit 240 designed as a Helmholtz damper, a pipe section 242 which forms a throughflow channel 244 which extends between the inlet opening 142 and the outlet opening 144 extends between the inlet opening 142 and the outlet opening 144 and through the through openings 154 and the chambers 148 and 150 extends. The pipe section 242 is in turn provided with a plurality of apertures 246 which connect to one or more damping chambers 248 and 250 annularly surrounding the pipe section 242 and lying in the chambers 148 and 150 and around the pipe section 242, the chambers 148 and 150 are formed in the muffler housing 200 in the same manner as in the above embodiments.

In a Helmholtz damper thus extending around the pipe section 242 annular volume of the damping chambers 248 and 250 via the each of the damping chambers 248 and 250 associated number of openings 246 is coupled to the flow channel 244, wherein the natural resonance of the Helmholtz resonator of the respective annular volume of the damping chamber 248 and 250, of the cross-sectional area with which the respective chamber is coupled to the flow channel 244, that is on the sum of each of the damping chambers 248 and 250 associated apertures 246 and the radial extent of the apertures 246 in the pipe section 242 depends.

The damping of the first silencer unit 240 can thus be determined by a suitable choice of the damping chambers 248 and 250 as well as the number of openings 246 in the pipe section 242.

With regard to the further detailed function of the Helmholtz resonator and the calculation of the frequencies, reference is made in its entirety to the book "Ingenieurakustik" by Henn, Sinambari, Fallen, 4 th revised edition, pages 304 to 309. Incidentally, in the fourth embodiment shown in FIG. 15, the second muffler unit 160 is still provided in the muffler housing 200, and the muffler housing 200 is also part of the combined housing 210 formed by the base housing 212 and the cover housing 214 in the same manner as in FIGS above embodiments is formed.

Incidentally, with respect to all other features of the refrigerant compressor according to the fourth embodiment, reference is made in full to the comments on the above embodiments

taken, wherein identical elements are provided with the identical reference numerals.

In a fifth embodiment of a refrigerant compressor according to the invention, shown in Fig. 16, the muffler unit 240 'also works as a Helmholtz damper, in the same manner as in the fourth embodiment, the pipe section 242 is provided, which has openings 246 and the flow channel 244 forms.

However, in this embodiment, the apertures 246 couple to three annular attenuation spaces 248, 250, and 252 of different sizes, thus providing the ability to adjust the attenuation to different frequencies of the compressed gas or refrigerant.

In this case, the number and the volume of the damping chambers 248, 250 and 252 vary depending on the frequencies to be damped.

In the extreme case, in a sixth embodiment, shown in FIG. 17, only a damping chamber 248 is provided, which is coupled via the openings 246 of the tube section 242 to the flow channel 244, wherein in this solution primarily the damping is tuned to a frequency. A variation of the sixth embodiment, shown in Fig. 18 as a seventh embodiment, additionally provides that in the

Damping space 248 "which is approximately identical to that of the sixth embodiment, still damping materials 260 are provided.

Incidentally, the seventh embodiment is formed in the same manner as the sixth embodiment, so that full content can be made to the comments on the sixth embodiment.

Claims

P A T E N T A N S P R E C H E

Comprising a refrigerant compressor

an overall housing (10),

a screw compressor (60) provided in the overall housing (10) with a compressor housing (12) formed as part of the overall housing (10) in which at least one screw rotor bore (64, 120) is arranged with at least one screw rotor bore (64, 120). screw rotors (62, 122) arranged to rotate about an axis of rotation (63, 123), with a suction-side bearing unit (74, 128) for the screw rotor (62, 122) arranged on the compressor housing (12), with at least one compressor housing (12 ) arranged on the pressure side bearing unit (72, 126) for the screw rotor (62, 122) and provided with a compressor housing (12) housing window (133) for compressed refrigerant,

and a first muffler unit (140) disposed in the overall housing (10).

That is, the first silencer unit (140, 240) is arranged adjacent to the housing window (133), and that the silencer unit (140, 240) is arranged.

at least one between an inlet opening (142) and a

Having outlet (144) lying and transversely to a flow direction relative to the inlet opening (142) and the outlet opening (144) widening chamber (148, 150, 248, 250).

Refrigeration compressor according to claim 1, characterized in that the first silencer unit (140, 240) in a to the compressor housing (12) in the region of the housing window (133)

subsequent muffler housing (200) is arranged.

3. refrigerant compressor according to claim 2, characterized in that the muffler housing (200), the housing window (133) tightly overlaps.

4. refrigerant compressor according to claim 2 or 3, characterized in that the muffler housing (200) itself the inlet opening (142), the outlet opening (144) and the at least one chamber (148, 150, 248, 250).

5. Refrigerant compressor according to one of the preceding claims,

characterized in that the muffler housing (200) next to a at least one pressure-side bearing unit (72, 126) receiving the bearing housing (68) is arranged.

6. refrigerant compressor according to one of the preceding claims,

characterized in that the muffler housing (200) is held on the compressor housing (12).

7. Refrigerant compressor according to one of the preceding claims,

characterized in that the muffler housing (200) and the bearing housing (68) are formed as parts of a combined housing (210).

8. refrigerant compressor according to claim 7, characterized in that the combined housing (210) has a base housing (212) and a

Cover housing (214).

9. refrigerant compressor according to claim 8, characterized in that the base housing (212) and the cover housing (214) by a transverse to the axis of rotation (63, 123) of the at least one screw rotor (62, 122) extending parting plane (2169 are separable.

10. refrigerant compressor according to claim 8 or 9, characterized in that in the base housing (212) at least a part of the bearing housing (68) and at least a part of the muffler housing (200) is formed.

11. Refrigerant compressor according to one of claims 8 to 10, characterized in that in the base housing (212) at least a portion of the chambers (148, 150) of the muffler unit (140, 240) is formed.

12. refrigerant compressor according to claim 11, characterized in that in the base housing (212) between the chambers (148, 150) lying partitions (152) are formed.

13. Refrigerant compressor according to one of claims 8 to 12, characterized in that the base housing (212) is an integral part.

14. Refrigerant compressor according to one of claims 8 to 13, characterized in that the cover housing (214) is an integral part.

15. Refrigerant compressor according to one of the preceding claims, characterized in that the first muffler unit (140, 240) has a to the outlet window (132) adjoining the receiving chamber (138), on which the inlet opening (142) follows.

16. Refrigerant compressor according to one of the preceding claims, characterized in that the first muffler unit (140) is arranged so that it can be flowed through by the compressing refrigerant in a flow direction (146) transversely to a pressure-side wall (78) of the compressor housing ( 12) and directed away from this.

17. Refrigerant compressor according to one of the preceding claims, characterized in that the muffler unit (140) is designed as a passage damper, which has at least one passage opening (142, 144, 154) and at least one expansion chamber following this passage opening (148, 150) and that the inlet opening (142) and the outlet opening (144) each have a passage opening and the at least one chamber (148, 150) forming at least one expansion chamber.

18. Refrigerant compressor according to claim 17, characterized in that the muffler unit (140) has a plurality of through openings (154), to each of which an expansion chamber (148, 150) follows.

19. A refrigerant compressor according to claim 17 or 18, characterized in that a plurality of the passage openings (142, 144, 154) of the muffler unit (140) have identical cross sections.

20. Refrigerant compressor according to one of claims 16 to 19, characterized in that the muffler unit (140) a plurality

Expansion chambers (148, 150) having different volume.

21. Refrigerant compressor according to claim 20, characterized in that the expansion chambers (148, 150) with different volume has a different extent in the flow direction (146).

22. Refrigerant compressor according to one of the preceding claims, characterized in that the silencer unit (240) extends from the inlet opening (142) to the outlet opening (144).

extending, a through-flow channel (244) forming tubular portion (242) which has shell-side openings (246) which in at least one in the at least one chamber (148, 150) arranged and adjacent to the pipe section damping chamber (248, 250) open.

23. A refrigerant compressor according to claim 22, characterized in that the pipe section (242) passes through a plurality of chambers (148, 150), each of which adjacent to the pipe section (242)

Damping chamber (248, 250) forms.

24. Refrigerant compressor according to claim 23, characterized in that the silencer unit (240) has at least two damping chambers (248, 250), which have a different volume.

25. Refrigerant compressor according to claim 24, characterized in that the damping chambers (248, 250) with different volumes have a different extent in the longitudinal direction of the pipe section (242).

26. Refrigerant compressor according to one of the preceding claims, characterized in that the muffler housing (200) within a pressure housing (16) of the overall housing (10) is arranged.

27. Refrigerant compressor according to claim 26, characterized in that the pressure housing (16) engages over the muffler housing (200).

28. Refrigerant compressor according to claim 27, characterized in that the muffler housing (200) is surrounded by a pressure housing (16) located in the pressure chamber.

29. Refrigerant compressor according to one of the preceding claims, characterized in that in the pressure housing (16) has a

Schmiermittelabscheideeinheit (180) is arranged.

30. A refrigerant compressor according to claim 29, characterized in that the Schmiermittelabscheideeinheit (180) downstream of the at least one silencer unit (140, 160, 240) is arranged.