EP3011181A1

EP3011181A1 - Refrigerant condenser

Info

Publication number: EP3011181A1
Application number: EP14730912.4A
Authority: EP
Inventors: Klaus Feller; Roni LÖRCH; Tihomir Mikulic
Original assignee: Bitzer Kuehlmaschinenbau GmbH and Co KG
Current assignee: Bitzer Kuehlmaschinenbau GmbH and Co KG
Priority date: 2013-06-18
Filing date: 2014-06-17
Publication date: 2016-04-27
Anticipated expiration: 2034-06-17
Also published as: CN105283669A; CN105283669B; WO2014202611A1; US20160097572A1; DE102013106344A1; EP3011181B1; RU2659420C2; DE102013106344B4; US10508839B2; RU2016101119A

Abstract

The invention relates to a refrigerant condenser, in particular a screw compressor, comprising a compressor housing (12), a compressor element (26, 28) which is driven by a drive and which is arranged in said compressor housing, at least one bearing unit (62, 64) for at least one element of the drive, comprising at least one bearing housing (116, 118) and at least one roller bearing (112, 114) arranged in the bearing housing. Said bearing housing is supplied with a lubricant from a lubricant distribution system (104) and is associated with a lubricant dosing unit (152, 154) which comprises a filter receiving chamber (182) and a filter body (184) is arranged in the filter receiving chamber.

Description

REFRIGERANT COMPRESSOR

The invention relates to a refrigerant compressor, in particular a

Screw compressor, comprising a compressor housing, arranged in the compressor housing and driven by a drive compressor element, at least one bearing unit for at least one element of the drive, which comprises at least one bearing housing and at least one arranged in the bearing housing rolling bearing.

Such refrigerant compressors are known from the prior art.

In these refrigerant compressors, there is the problem that the rolling bearing in the bearing housing on the one hand should be optimally lubricated, on the other hand, a supply of too much lubricant in turn leads to power losses of the compressor.

The invention is therefore based on the object to improve a refrigerant compressor of the type described above such that an optimal supply of lubricant to the rolling bearing in the bearing housing is possible.

This object is achieved in a refrigerant compressor of the above

described type achieved in that the bearing housing is supplied by a lubricant distribution system lubricant, that the bearing housing is assigned a Schmiermitteldosiereinheit having a filter receiving chamber, and that in the filter receiving chamber, a filter body is arranged.

The advantage of the solution according to the invention is the fact that with this the possibility exists to meter through the filter body the flow of lubricant to the rolling bearing in the bearing housing and at the same time still reduce the likelihood of damage to the bearing, the lubricant flow is again filtered through the filter body immediately before it enters the rolling bearing, so that even particles floating in the lubricant distribution system can be filtered out and can not enter the rolling bearing.

In connection with the above explanation of the individual

Components of the lubricant metering unit have not been given any further details on the formation of the same with regard to additional elements for the filter body receptacle and the filter body.

In particular, it was assumed that the filter body assumes the throttling function for the flow of the lubricant. In the simplest case, it is provided that, following the filter receiving chamber, an inlet channel extends from the filter receiving chamber to a lubricant chamber adjoining the rolling bearing.

This inlet channel has to take over in the simplest case, no additional functions.

However, another advantageous solution provides that the Schmiermitteldosiereinheit arranged between the filter receiving chamber and adjacent to the rolling bearing lubricant chamber throttle bore, which in addition to the filter body has a throttling effect on the lubricant chamber supplied lubricant flow, so that overall the throttling effect of the Schmiermitteldosiereinheit through the filter body and the throttle bore is created.

Such a throttle bore has the advantage that its throttle effect can be supplemented with the throttling action of the filter body and thus can also be ensured for different operating states of a reliable lubricant distribution system of the rolling bearing in the bearing housing. In particular, in this case, the filter body not only has a throttling effect on the lubricant flow, but the filter body allows to perform the throttle bore as a very thin fine bore, without the risk that this throttle bore clogged due to particles distributed by the lubricant system entrained particles ,

With regard to the arrangement of the lubricant metering unit, no further details have been given so far.

In principle, it would be conceivable to provide the lubricant metering unit in front of the bearing housing in the lubricant distribution system.

However, a favorable solution provides that the lubricant metering unit is integrated in the bearing housing.

A particularly expedient solution provides that the bearing housing has a housing element in which the lubricant metering unit is arranged, in particular integrated, is.

In this case, the housing element could be, for example, a housing section receiving the roller bearing.

However, another advantageous solution provides that the housing element, which receives the lubricant metering unit, is designed as a bearing housing cover of the bearing housing.

A further advantageous solution provides that the housing element is designed as a bearing housing ring of the bearing housing.

In particular, in this case, the lubricant metering unit is integrated in the bearing housing cover. With regard to the guidance of the lubricant in the bearing housing so far no further details have been made.

Thus, a solution provides that the lubricant metering unit supplies the lubricant to a lubricant chamber of the bearing housing, from which the lubricant can then enter the rolling bearing.

In the simplest case, it is provided that the lubricant metering unit supplies the lubricant to the lubricant chamber, wherein the lubricant collects at a lowest point of the lubricant chamber and then enters the rolling bearing.

Another advantageous solution provides that the Schmiermitteldosiereinheit is provided with a filter receiving chamber downstream nozzle bore, which directed a to the rolling bearing in the bearing housing

Produced lubricant jet and thus selectively applying the lubricant, for example, to the rolling elements of the bearing.

In this case, the filter body according to the invention has a further advantage, namely to the effect that the nozzle bore can be formed as a very fine bore and due to the additional filtering effect of the filter body clogging of the nozzle bore is avoided by distributed in the lubricant system entrained particles.

A particularly favorable solution provides that the throttle bore of the

Lubricant metering unit is arranged so that it acts as a nozzle bore.

In the solution according to the invention, the filter body may be formed of different materials. One possibility is to form the filter body from sintered metal, for which purpose bronze or stainless steel can be used as the material.

Another possibility provides to form the filter body of refrigerant and lubricant neutral plastic, in particular, a sintered porous plastic, for example, a compacted or baked plastic granules, can be used.

To the compressor element and to the drive so far no further details have been made.

Thus, the compressor element could be a piston or a scroll element, with a correspondingly designed drive for this.

An advantageous solution provides that the compressor element a

Screw rotor of a screw compressor is and that the drive comprises as elements the screw rotor bearing shaft sections, of which at least one is mounted according to the present invention.

In particular, the arranged on the suction side and / or the high-pressure side arranged shaft sections are stored according to the present invention.

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

In the drawing show:

1 shows a schematic longitudinal section through a first embodiment of a refrigerant compressor according to the invention. an enlarged sectional view corresponding to Figure 1 in the region of suction side arranged storage units. an enlarged section through a first embodiment of a bearing housing cover according to the invention; a section similar to FIG. 3 through a second embodiment of a bearing housing cover according to the invention; a section through a third embodiment of a bearing housing cover according to the invention; a schematic longitudinal section similar to FIG. 1 through a second embodiment of a refrigerant compressor according to the invention; an enlarged sectional view corresponding to Figure 6 in the region of high pressure side bearing units. an enlarged section similar to FIG. 3 through a first embodiment of a bearing housing ring according to the invention; an enlarged section similar to FIG. 8 through a second embodiment of a bearing housing ring according to the invention and a section similar to FIG. 8 through a third embodiment of a bearing housing ring according to the invention. An in Fig. 1 illustrated embodiment of a refrigerant compressor according to the invention comprises an overall housing 10, which has a compressor housing 12, a motor housing 14 arranged on one side of the compressor housing 12 and a pressure housing 16.

In the compressor housing 12 are receiving bores 22, 24 for

Screw rotors 26 and 28 are provided which are rotatably mounted in the receiving bores 22, 24 about axes of rotation 32, 34.

The screw rotors 26, 28 extend from a low-pressure side 36 to a high-pressure side 38, wherein the low-pressure side 36 is associated with a refrigerant supply passage 42, while on the high-pressure side 38 a in FIG. 1 is provided, from which the compressed refrigerant via a discharge channel 44 enters the pressure housing 16, in an end-side chamber 46, from which it then passes through two arranged in the pressure housing 16 Schmiermittelabscheider 52, 54, through which the lubricant separated from the compressed refrigerant and an arranged in the pressure housing 16 oil sump 56 is supplied, wherein also the high pressure compressed refrigerant exits through a high-pressure outlet, not shown, from the pressure housing 16.

The bearing of the screw rotor 26, 28 takes place in the region of the low pressure side 36 of the screw rotor 26, 28 by arranged in the compressor housing bearing units 62, 64, which bearing shaft sections 66, 68 of the screw rotor 26, 28 store.

Furthermore, a bearing of the screw rotor 26, 28 in the region of its high pressure side by bearing units 72, 74, which also shaft portions 76, 78 of the screw rotor 26, 28 store. The bearing units 72, 74 are arranged in a high-pressure side bearing housing 82 which is fixedly connected to the compressor housing 12 and projects into the pressure housing 16 following the compressor housing 12.

The screw rotors 26, 28 are driven by a drive motor 84 arranged in the motor housing 14, the motor shaft 86 of which, for example, integrally merges with the bearing shaft section 66 and carries a rotor 92, which in this exemplary embodiment is also rotatable coaxially with the axis of rotation 32 of the bearing shaft section 66.

Furthermore, the drive motor 84 has a stator 96, which is arranged rotationally fixed in the motor housing 14.

For example, in the illustrated embodiment of the refrigerant compressor according to the present invention, the drawn refrigerant first flows through the motor housing 14 to cool the rotor 92 and the stator 94, and then enters the refrigerant supply passage 42 which supplies the low pressure side refrigerant 36 of the screw rotors 26, 28 feeds.

For lubrication of all bearing units 62, 64 and 72, 74 as well as the screw rotors 26, 28 in the receiving bores 22, 24 a designated as a whole with 100 lubricant supply system is provided, which receives lubricant from the lubricant sump 56, which is under high pressure, a filter unit 102 and then supplies the lubricant from the filter unit 102 to the individual bearing units 62, 64, 72, 74.

In particular, the lubricant supply system 100 comprises a lubricant distribution system 104 leading from the filter unit 102 to the storage units 62, 64. To be able to lubricate the bearing units 62, 64 optimally by the lubricant distribution system 104, the bearing shaft sections 66, 68 rotatably receiving rolling bearings 112, 114 respectively in bearing housings 116, 118 arranged on the one hand by bearing outer rings 122, 124 of the roller bearings 112, 114 receiving and Receiving bores 126, 128 provided wall portions 132, 134 of the compressor housing 12 are formed and on a the

respective screw rotor 26, 28 facing away by bearing housing cover 136, 138 are closed, so that in the bearing housings 116, 118 lubricant chambers 142, 144 are present, to which the lubricant for lubricating the bearings 112, 114 is to be supplied.

These lubricant chambers 142, 144 on the one hand lubricant is sufficiently supplied to a reliable and durable

Lubricating the rolling bearings 112, 114 to ensure on the other hand, but too much lubricant chambers 142, 144 supplied lubricant splashing and crushing in the rolling bearings 112, 114, which increase the power consumption of the drive motor 84 and thus deteriorate the coefficient of performance of the refrigerant compressor.

Therefore, it is necessary to ensure a metered supply of lubricant from the lubricant distribution system 104.

For this purpose, each of the bearing housings 116, 118 is provided with a lubricant metering unit 152, 154, which is integrated, for example, in the respective bearing housing cover 136, 138.

The function and mode of operation of the lubricant metering units 152, 154 will be explained below by way of example with reference to the lubricant metering unit 154 integrated in the bearing housing cover 138, with the corresponding embodiments for the lubricant metering unit 152 integrated in the bearing housing cover 136. As shown in FIG. 3, the bearing housing cover 138 comprises an outer annular body 162, which is inserted with its radially outer peripheral surface 164 in the respectively corresponding receiving bore, in this case the receiving bore 128. An end wall designated as a whole by 166 is formed on the annular body 162 and delimits an inner space 168 enclosed by the annular body 162 on a side facing away from the respective screw rotor 26, 28, while the inner space 168 faces the respective rolling bearing, in this case the rolling bearing 114 an opening 172, so that the corresponding lubricant chamber 144 may extend into the interior 168 inside.

Further, the annular body 162 includes a circumferential groove 174 extending into it from the peripheral surface 164, which serves to pass the lubricant supplied from the lubricant distribution system 104, for example, to the bearing housing cover 138.

The lubricant metering unit 154 comprises in the first embodiment shown in FIG. 3 thereof a filter receiving chamber 182 extending into the annular body 162 starting from the groove 174 and into which a filter body 184 is inserted.

From the filter receiving chamber 182 extends, preferably coaxially to this, an inlet channel 186 to the interior 168th

For example, in this case the filter receiving chamber 182 and the inlet channel 186 are designed as bores, wherein the filter receiving chamber 182 relative to a central axis 188 has a larger diameter than the adjoining these coaxially adjacent inlet channel 186, so that during the transition from the filter receiving chamber 182 in the inlet channel 186th a step 192 forms, against which the filter body 184 and by which the filter body 184 is secured against migration into the interior 168. The filter body 184 is preferably made of a porous material, so that the filter body 184 by selecting the porosity thereof as

Flow restrictor for the supplied lubricant acts and is thus able to throttle the lubricant supply into the corresponding lubricant chamber 144 so that sufficient lubricant, but not too much lubricant, the respective lubricant chamber, in this case the

Lubricant chamber 144, is supplied.

The filter body 184 may be formed of different materials.

One possibility is to form the filter body 184 of sintered metal, for which purpose bronze or stainless steel can be used as the material.

Another possibility provides to form the filter body 184 of refrigerant and lubricant neutral plastic, in particular a sintered porous plastic, and / or a compacted baked plastic granules, can be used.

In the first exemplary embodiment of the lubricant metering unit 154 according to the invention, the inlet channel 186 adjoining the filter receiving chamber 182 does not impede the flow, but is irrelevant to the question of metering the amount of lubricant supplied to the lubricant chamber 144.

The lubricant collects, for example, then at least partially in the lubricant chamber 144 at the lowest point in the direction of gravity in the form of a lubricant bath 190 and passes from this into the rolling bearing 114. In a second embodiment of a Schmiermitteldosiereinheit 154 'according to the invention, shown in Fig. 4, which adjoins the filter receiving chamber 182 inlet channel 186 does not open directly into the interior 168 of the annular body 162, but passes into a throttle bore 194, which in addition to the filter body 184 a Has throttling effect on the supplied lubricant flow, so that in this case the Schmiermitteldosiereinheit 154 'on the one hand exerts a throttling effect by the filter body 184 and on the other hand through the throttle bore 194, wherein the throttle bore 194 preferably radially to the axis of rotation 34 of the corresponding rolling bearing, in this case the rolling bearing 114th , is aligned.

In a third exemplary embodiment of a lubricant metering unit 154 "according to the invention, illustrated in FIG. 5, the inlet channel 186 running radially to the axis of rotation 34 of the associated rolling bearing 114 merges into a nozzle bore 196 which lies within the opening 172 of the interior 186 facing the roller bearing 114, However, in particular parallel or slightly oblique to the axis of rotation 34 of the associated rolling bearing 114 extends and thus a directly on the rolling bearing 114, in particular on rolling elements thereof, directed lubricant jet 198 is generated, so that a direct supply of lubricant to the rolling bearing 114 takes place to the

Lubricant distribution in the rolling bearing 114 to optimize.

In this case, for example, the inlet channel 186 is closed to the interior 168 of the annular body 162 out.

In a second embodiment of a screw compressor according to the invention, shown in FIG. 6, all those parts which are identical to those of the first embodiment are given the same reference numerals, so that reference may be made to the description of the same with respect to the embodiments of the first embodiment. Unlike the first embodiment, the lubricant distribution system 104 "" supplies lubricant to not only the bearing units 62 and 64 but also the bearing units 72 and 74.

As in FIG. 6 and enlarged in FIG. 7, each of the bearing units 72 and 74 includes a set of rolling bearings 202, 204 and 206 disposed in the high pressure side bearing housing indicated as a whole by 82 and with their bearing outer rings 212, 214, 216 in respective receiving bores 222 and 224 the bearing housing 82 are seated, wherein the receiving bores 222, 224 of wall portions 226, 228 of the high-pressure side bearing housing 82 are surrounded and also on their the high pressure sides 38 of the screw rotor 26, 28 side facing by wall portions 232, 234 bounded by the shaft portions 76 and 78 and close tightly with these, so that the wall portions 232, 234 form a tight seal between the high-pressure sides 38 of the screw rotors 26, 28 and the receiving bores 222, 224.

On the high pressure sides 38 of the screw rotors 26, 28 opposite sides of the wall portions 232, 234 sit in the receiving bores 222, 224 used Lagergehäuseringe 242, 244, which are thus arranged between the respective wall portions 232, 234 and the respective nearest rolling bearing 202.

Such Lagergehäuseringe 242, 244 can either, as shown in FIG. 6 and 7, the ends of the rolling bearings 202, 204,206 be arranged or between two of the rolling bearings 202, 204, 206th

The bearing housing rings 242, 244 define lubricant chambers 252, 254 arranged between these and the closest rolling bearings 202, from which lubricant is supplied to the roller bearings 202, 204 and 206, for example through the respective bearings. As shown in FIG. 8 in a first exemplary embodiment of the bearing housing ring 244, each of these bearing housing rings 242, 244 comprises an annular body 262 having a circumferential surface 264 adjacent to the wall regions 226, 228 and an inner space 266 opposite the peripheral surfaces 264, which is part of the respective lubricant chamber 254 is.

Further, starting from the peripheral surface 264 into the annular body 262, a groove 274 extends in the same manner as in the bearing housing covers 136, 138.

Further, starting from the groove 274, the filter receiving chamber 182 extends to the filter body 184 and an adjacent to the filter receiving chamber 182 inlet channel 186, which opens into the interior 266 of the bearing housing ring 244.

Starting from the groove 274, which has the same task as in

In connection with the bearing housing covers 136, 138, the lubricant metering unit 152, 154 is thus also provided in each of the bearing housing rings 242, 244, which has the filter receiving chamber 182 extending into the annular body 262 from the groove 274, into which the filter body 144 is inserted is and from which the inlet channel 186 extends to the interior 266 of the bearing housing ring 244.

Here, the Schmiermitteldosiereinheit 152, 154 is formed in the same way as described in the preceding embodiments and has the same effect as in also explained in connection with these embodiments.

The bearing housing ring 244 may also be inserted between two of the rolling bearings 202, 204, 206. In a second embodiment of the bearing housing ring 244 ', shown in Fig. 9, the Schmiermitteldosiereinheit 154 "is formed in the same manner as described in the third embodiment of the bearing housing cover 136, 138 of the first embodiment of the refrigerant compressor according to the invention, so that the description of the third embodiment can be taken fully content, wherein the Schmiermitteldosiereinheit 154 "is integrated in this case in the annular body 262 and the annular body 262 has no inner space 266. Instead, the ring body 262 has the outgoing from the inlet channel 186 and into the lubricant chamber 254 directed into the first roller bearing 202 nozzle bore 196 which generates the lubricant jet 198, which is directed in particular to rolling elements of the first rolling bearing 202.

A third exemplary embodiment of a bearing ring 244 "according to the invention, shown in FIG. 10, is designed such that it can be inserted between two of the roller bearings 202, 204, 206, wherein opposing nozzle bores 196a, b are provided, each having a lubricant jet 198a , b so that the lubricant jets 198a, b propagate in opposite directions.

Incidentally, the third embodiment is formed in the same manner as the second embodiment, so that reference is made to this entirety.

Claims

PATENT APPLICATION HE

1. refrigerant compressor, in particular screw compressor, comprising a compressor housing (12), in the compressor housing (12) arranged and by a drive (84, 86, 66, 68, 76, 78) driven compressor element (26, 28), at least one storage unit (62, 64, 72, 74) for at least one element (66, 68) of the drive (84, 86, 66, 68, 76, 78), which at least one bearing housing (116, 118, 82) and at least one in the Bearing housing (116, 118, 82) arranged rolling bearing (112, 114, 202, 204, 206),

characterized in that lubricant is supplied to the bearing housing (116, 118, 82) by a lubricant distribution system (104), that a lubricant metering unit (152, 154) is associated with the bearing housing (116, 118, 82), which has a filter receiving chamber (182), and that a filter body (184) is disposed in the filter receiving chamber (182).

Second refrigerant compressor according to claim 1, characterized in that the Schmiermitteldosiereinheit (152, 154) has an inlet channel (186) which extends from the filter receiving chamber (182) to a to the rolling bearing (112, 114, 202) adjacent the lubricant chamber (142 , 144, 252, 254).

3. refrigerant compressor according to claim 1 or 2, characterized in that the Schmiermitteldosiereinheit (152, 154) one between the filter receiving chamber (182) and one of the rolling bearing (112, 114, 202) adjacent the lubricant chamber (142, 144, 252, 254) arranged throttle bore (194).

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

characterized in that the lubricant metering unit (152, 154) is integrated in the bearing housing (116, 118, 82).

5. Refrigerant compressor according to claim 4, characterized in that the bearing housing (116, 118, 82) has a housing element (136, 138, 242, 244), in which the Schmiermitteldosiereinheit (152, 154) is arranged.

6. refrigerant compressor according to claim 5, characterized in that the housing element is a bearing housing cover (136, 138) of the bearing housing (116, 118).

7. refrigerant compressor according to claim 5, characterized in that the housing element is a bearing housing ring (242, 244) of the bearing housing (82).

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

characterized in that the lubricant metering unit (152, 154) supplies the lubricant to the lubricant chamber (142, 144, 252, 254).

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

characterized in that the lubricant metering unit (152, 154) is provided with a nozzle bore (196) disposed downstream of the filter receiving chamber (182), which has a lubricant jet directed onto the rolling bearing (112, 114, 202) in the bearing housing (116, 118, 82) (198) generated.

10. refrigerant compressor according to claim 9, characterized in that the nozzle bore (196) simultaneously acts as a throttle bore of the Schmiermitteldosiereinheit (152, 154).

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

characterized in that the compressor element is a screw rotor (26, 28) of a screw compressor.