EP1828603B1 - Hermetic refrigerant compressor - Google Patents

Abstract

The invention relates to a hermetically enclosed refrigerant compressor having a hermetically tight compressor housing inside of which a piston/cylinder unit that compresses a refrigerant operates with a suction valve having a suction opening located in a valve plate of the unit. A suction sound damper having a filling volume is provided on the cylinder head of the piston/cylinder unit and refrigerant flows to the suction valve of the piston/cylinder unit via this suction sound damper. To this end, the suction sound damper has an entry cross-section via which refrigerant flows into the suction sound damper, and a compensation volume is provided, which is connected to the suction sound damper and to the interior of the compressor housing, and inside of which refrigerant oscillates. The compensation volume equals 0.5 to 3 times the displacement of the piston of the piston/cylinder unit.

Description

The present invention relates to a hermetically sealed refrigerant compressor, which has a hermetically sealed compressor housing in the interior of which a refrigerant-compressing piston-cylinder unit operates on the cylinder head, a suction muffler (Muffler) is arranged, via the refrigerant to the intake valve of the piston-cylinder Unit flows according to the preamble of claim 1.

State of the art

Such refrigerant compressors have long been known and are mainly used in refrigerators or shelves. Accordingly high is the annually produced quantity.

Although the energy consumption of a single refrigerant compressor is only between 50 and 150 watts, when considering all refrigerating compressors in use worldwide, very high energy consumption results, which is steadily increasing in poorer countries due to the rapid development.

Every technical improvement that is made to a refrigerant compressor and increases the efficiency, thus, when extrapolated to the refrigerant compressors used worldwide, harbors an enormous energy saving potential.

The refrigerant process as such has long been known. The refrigerant is thereby heated by energy consumption from the space to be cooled in the evaporator and finally superheated and pumped by the refrigerant compressor to a higher pressure level, where it emits heat through a condenser and via a throttle, in which a pressure reduction and the cooling of the refrigerant, is transported back into the evaporator.

The biggest and most important potential for a possible improvement of the efficiency lies in the lowering of the temperature of the refrigerant at the beginning of its compression process. Each reduction of the suction temperature of the refrigerant in the cylinder of the piston-cylinder unit therefore causes as well as the lowering of the temperature during the compression process and, associated with the Ausschiebetemperatur a reduction in the required technical work for the compression process.

In known hermetically sealed refrigerant compressors is due to design a strong heating of the refrigerant on its way from the evaporator (refrigerator) to the intake valve of the piston-cylinder unit.

The suction of the refrigerant takes place via a suction pipe coming directly from the evaporator during an intake stroke of the piston-cylinder unit. The suction pipe opens in known hermetically sealed refrigerant compressors usually in the hermetically sealed compressor housing, usually in the vicinity of the inlet cross section in the suction muffler, from where the refrigerant flows into the suction muffler and from this directly to the intake valve of the piston-cylinder unit. The suction muffler serves primarily to keep the noise level of the refrigerant compressor during the intake as low as possible. Known suction mufflers are usually made of several volumes that communicate with each other, and an inlet cross-section, through which the refrigerant is sucked from the hermetically sealed compressor housing volume in the interior of the suction muffler, and an opening which is close to the intake valve of the piston-cylinder Unit is present.

On the way between entry of the refrigerant in the compressor housing and the intake valve of the piston-cylinder unit takes place, as already mentioned, a - not desirable - heating of the refrigerant. Measurements have shown that, for example, at a refrigerant temperature of 32 ° C in the intake manifold (given by standardized Ashrae conditions) just before entering the compressor housing, the refrigerant was already heated in the first Saugschalldämpfervolumen to a temperature of about 54 ° C. The main cause of this undesirable heating of the refrigerant is the fact that the fresh refrigerant flowing from the suction pipe into the compressor housing is mixed with warmer refrigerant already in the compressor housing. The mixture arises essentially in that the intake valve of the piston-cylinder unit per cycle is open only over a crank angle range of about 180 ° and therefore only within this time window refrigerant can be sucked into the cylinder of the refrigerant compressor. Thereafter, during the compression cycle, the intake valve is closed. However, the cold refrigerant has an almost constant mass flow, even with the intake valve closed, whereby it flows with the intake valve closed and flows into the compressor housing and the moving in-motion piston-cylinder unit and their components, which in turn, however, a heating of the Refrigerant itself causes. In addition, due to the pressure oscillations during the compression phase, further flow processes from the compressor housing to the suction muffler and vice versa, whereby an additional mixing is effected.

In order to prevent this mixing of hot refrigerant from the interior of the compressor housing with refrigerant coming fresh from the evaporator, in known refrigerant compressors, the outlet of the suction pipe for the refrigerant is placed in the vicinity of the inlet cross section of the suction muffler. This ensures that relatively little cold refrigerant can escape from the evaporator into the interior of the compressor housing. In a further consequence one has the Saugrohrende designed so that in this an intermediate tube could be introduced. At the same time, the intermediate tube was surrounded by a spiral spring, which is supported on the one hand at the inlet of the suction tube into the housing and on the other hand on the intermediate tube to achieve the connection of the suction tube to the suction muffler. However, all these known attempts to prevent mixing of the cold refrigerant from the evaporator with the heated refrigerant inside the compressor housing have only caused a reduction in this mixing, but not a complete inhibition.

From the WO 03/038280 It is known to connect the inlet cross-section of the suction muffler directly to the outlet of the suction pipe, so that the coming of the evaporator refrigerant is fed directly into the suction muffler without getting into the interior of the compressor housing and to heat there. Due to the fact already mentioned that the cold refrigerant, even with the intake valve closed, has an almost constant mass flow and flows into the suction muffler - now via the direct connection, it is then necessary to provide a compensating volume in the suction muffler in order to increase the pressure in the Due to the continuously flowing refrigerant, the intake silencer can be compensated from the intake manifold and via which the refrigerant located in the intake silencer can again flow out of it into the compressor housing. At the next Ansuagtakt then on the one hand located in the suction muffler or from the suction pipe in the suction muffler flowing refrigerant through the intake valve in the piston-cylinder unit sucked, but on the other hand - by leakage from the piston-cylinder unit and by the mentioned Outflow from the suction muffler - Refrigerants inside the compressor housing are in the equalizing volume for pressure equalization.

However, the flow conditions occurring, especially when overflowing into the compensating volume, which would not exist without a direct connection of intake manifold with the suction muffler, however, involve the risk of increased flow losses.

Object of the invention

The aim of the present invention is therefore to avoid this disadvantage and to provide a refrigerant compressor of the type mentioned, in which the refrigerant temperature at the beginning of the compression process, and thus necessarily when sucking into the cylinder of the piston-cylinder unit, is kept as low as possible , Wherein the flow losses are kept as far as possible during intake. It is a further object of the present invention to minimize the pressure fluctuations occurring in the interior of the compressor housing and in the suction muffler and to keep the noise level as low as possible when flowing over into the equalizing volume.

This is made possible by the characterizing features of claim 1 according to the invention.

By creating a compensation volume with a volume which is 0.5 to 3 times the stroke volume of the piston of the piston-cylinder unit, it is guaranteed that the refrigerant coming from the intake manifold does not enter the compressor housing even when the intake valve is closed there mixed with the already heated refrigerant. At the same time, it is guaranteed that no refrigerant is sucked out of the compressor housing via the compensating volume into the suction muffler or into the cylinder during the intake process.

In addition, the associated with the creation of the compensation volume due to the flow processes in the compensation volume and in the compressor housing noise be minimized so that it does not disturb the operator disturbing noise, which is particularly important for household refrigerators. Furthermore, a slightly larger compensation volume production technology can be made easier.

According to the characterizing features of claim 2, it is provided that the smallest flow cross-section in the compensation volume has a cross-sectional area which corresponds to 1/4 to 3/4 of the cross-sectional area of the intake opening. This ensures that the pressure difference is small, thereby reducing the flow losses and on the other hand, the noise attenuation to the outside is large.

According to the characterizing feature of claim 3, the cross section of the compensation volume may not exceed 1.5 times the piston bottom surface. This ensures that on the one hand the space required for the compensation volume is not too large and on the other hand it ensures that cold and warm suction gas does not mix or forms the boundary layer described below. -

The characterizing features of claim 4, according to which the compensating volume has a circular cross-section and the ratio of the length of the compensating volume to its diameter is greater than 10, describe a preferred embodiment, which causes particularly low flow losses.

In order to achieve a compact design as possible of the suction muffler despite additional compensating volume, the characterizing features of claim 5 are provided, according to which the compensating volume is formed by a cross-sectionally substantially U-shaped compensating tube, which at least partially wraps around the suction muffler.

The characterizing features of claims 6 to 9 describe a preferred embodiment of the connection of intake manifold and inlet cross-section in the suction muffler.

The characterizing features of claims 10 and 11 describe two different embodiments of a hermetically sealed refrigerant compressor, in which the inlet cross section is formed in the suction muffler and the transition from suction muffler in the compensating volume once separated and once coincides. Depending on the space required inside the compressor housing, the most advantageous embodiment variant is to be selected here, wherein in the case where the inlet cross section in the suction muffler and the transition of suction muffler in the equalization volume coincide another preferred embodiment according to the characterizing features of claims 12 to 14 is provided , This variant has the advantage that a tight connection between the intake manifold and suction muffler is not required.

Fig.1

eine Vorderansicht eines erfindungsgemäßen hermetisch gekapselten Kältemittelverdichters mit geschnittenem Verdichtergehäuse

Fig.2

eine Seitenansicht eines erfindungsgemäßen hermetisch gekapselten Kältemittelverdichters im Schnitt

Fig.3

eine Vorderansicht eines erfindungsgemäßen hermetisch gekapselten Kältemittelverdichters im Schnitt

Fig.4

eine Schnittansicht eines Saugschalldämpfers nach dem Stand der Technik

Fig.5

eine weitere Schnittansicht eines bekannten Saugschalldämpfers

Fig.6

eine Schnittansicht eines erfindungsgemäßen Saugschalldämpfers bei geschlossenem Ansaugventil

Fig.7

eine Schnittansicht eines erfindungsgemäßen Saugschalldämpfers bei offenem Ansaugventil

Fig.8

zeigt eine Schrägansicht des erfindungsgemäßen Saugschalldämpfers im Verdichtergehäuse

Fig.9

eine alternative Ausführungsvariante eines erfindungsgemäßen Saugschalldämpfers

Fig.9a

eine weitere alternative Ausführungsvariante eines erfindungsgemäßen Saugschalldämpfers

Fig.10

eine zusätzliche alternative Ausführungsvariante eines erfindungsgemäßen Saugschalldämpfers

Fig.11

eine Detailansicht einer hermetisch dichten Verbindung zwischen Saugschalldämpfer und Saugrohr

Fig.12

zeigt eine Detailansicht einer alternativen Ausführungsvariante einer hermetisch dichten Verbindung zwischen Saugschalldämpfer und Saugrohr

Fig.13

zeigt eine Detailansicht einer weiteren alternativen Ausführungsvariante einer hermetisch dichten Verbindung zwischen Saugschalldämpfer und Saugrohr

Fig.14

eine Detailansicht einer Verbindung eines Kunststoffschlauches mit einem Saugrohr

Fig.15

eine Detailansicht einer Verbindung eines Kunststoffschlauches mit einem Saugrohr

Fig.16

eine Detailansicht einer Verbindung eines Kunststoffschlauches mit einem Saugrohr

Fig.17

eine Detailansicht einer Verbindung eines Kunststoffschlauches mit einem Saugrohr

Fig.18

eine Detailansicht einer Verbindung eines Kunststoffschlauches mit einem Saugrohr

Fig.19

eine Schrägansicht eines alternativen erfindungsgemäßen Saugschalldämpfers

Fig.20

eine weitere Schrägansicht des erfindungsgemäßen Saugschalldämpfers aus Fig.19

Fig.21

eine Schnittansicht des erfindungsgemäßen Saugschalldämpfers aus Fig. 19

Fig.22

eine weitere Schnittansicht des erfindungsgemäßen Saugschalldämpfers aus Fig.19

Following is now a detailed description of the invention. Showing:

Fig.1

a front view of a hermetic-type refrigerant compressor according to the invention with cut compressor housing

Fig.2

a side view of a hermetically sealed refrigerant compressor according to the invention in section

Figure 3

a front view of a hermetically sealed refrigerant compressor according to the invention in section

Figure 4

a sectional view of a suction muffler according to the prior art

Figure 5

another sectional view of a known suction muffler

Figure 6

a sectional view of a suction muffler according to the invention with a closed intake valve

Figure 7

a sectional view of a suction muffler according to the invention with open intake valve

Figure 8

shows an oblique view of the suction muffler according to the invention in the compressor housing

Figure 9

an alternative embodiment of a suction muffler according to the invention

9a

a further alternative embodiment of a suction muffler according to the invention

Figure 10

an additional alternative embodiment of a suction muffler according to the invention

Figure 11

a detailed view of a hermetically sealed connection between suction muffler and intake manifold

Figure 12

shows a detailed view of an alternative embodiment of a hermetically sealed connection between the suction muffler and intake manifold

Figure 13

shows a detailed view of another alternative embodiment of a hermetically sealed connection between the suction muffler and intake manifold

Figure 14

a detailed view of a compound of a plastic tube with a suction tube

Figure 15

a detailed view of a compound of a plastic tube with a suction tube

Figure 16

a detailed view of a compound of a plastic tube with a suction tube

Figure 17

a detailed view of a compound of a plastic tube with a suction tube

Figure 18

a detailed view of a compound of a plastic tube with a suction tube

Figure 19

an oblique view of an alternative Saugschalldämpfers invention

fig.20

a further oblique view of the suction muffler according to the invention Figure 19

Figure 21

a sectional view of the suction muffler according to the invention Fig. 19

Figure 22

a further sectional view of the suction muffler according to the invention Figure 19

Fig.1, 2 and 3 each show a sectional view through a hermetically sealed refrigerant compressor, wherein Fig.1 and 3 each one view in the direction of arrow A from Fig.2 represents. Inside a hermetically sealing compressor housing 1, a piston-cylinder engine unit is mounted elastically via springs 2.

The piston-cylinder-motor unit consists essentially of a cylinder housing 3 and the therein a lifting movement performing piston 4, and a crankshaft bearing 5, which is arranged perpendicular to the cylinder axis 6. The crankshaft bearing 5 receives a crankshaft 7 and protrudes in a centric bore 8 of the rotor 9 of an electric motor 10. At the upper end of the crankshaft 7 is a connecting rod bearing 12, via which a connecting rod and subsequently the piston 4 is driven. The crankshaft 7 has a lubricating oil bore 13 and is fixed in the region 14 on the rotor 9. On the cylinder head 15 of the suction muffler 16 is arranged to reduce the noise during the intake of the refrigerant to a minimum.

Figure 4 shows a sectional view through a suction muffler 16 according to the prior art. The suction muffler 16 is, as already out of the Fig.1,2 and 3 can be seen, arranged inside the hermetically sealed compressor housing 1 on the cylinder head 15. Coming from the evaporator, compared to the located in the compressor housing 1 warm refrigerant, cold refrigerant flows when using such a known suction muffler 16 via a suction pipe 17 in the interior of the compressor housing 1 in the vicinity of the inlet cross section 18 of the suction muffler 16, where it is mixed with the already located in the compressor housing 1, warm refrigerant and heated.

Suction mufflers 16 according to the prior art generally consist of a plurality of series-connected and / or parallel-connected volumes V1, V2, V _n , which are connected to each other via tubes, and a Ölabscheideöffnung 31 at the lowest point. The cold refrigerant flows via the suction pipe 17 into the interior of the compressor housing 1 where, due to the design, a first mixing takes place with the hot refrigerant already present in the compressor housing 1. Then, the already mixed and heated refrigerant flows through the inlet cross section 18 in the first volume V1 and then in the second volume V2 of the suction muffler 16 and mixes again in both V1 and V2 with the already existing there warm refrigerant, thereby again heating the refrigerant takes place. In these known Suction mufflers is the heating between the outlet of the suction pipe 17 and just before the suction port 24 in the suction muffler 16 between 30K and 40K, depending on the performance of the refrigerant compressor.

Figure 5 shows a likewise from the prior art, namely from the WO03 / 038280 known suction muffler 16, the inlet cross section 18, however, is tightly connected to the suction pipe 17. As a result, the cold refrigerant coming from the suction pipe 17 can not mix with the warmer refrigerant located in the compressor housing 1 before it is sucked into the suction muffler 16.

To the suction muffler 16, a compensating volume 21 is connected, via which the required due to the direct connection of the suction muffler 16 with the suction pipe 17 pressure equalization can take place in which a connection to both the suction muffler 16 and in the interior of the compressor housing. Due to the required pressure equalization, however, flow states of the refrigerant occur, which can lead to flow losses which negate the energy gain which is achieved by the reduction of the refrigerant temperature at the beginning of the compression phase.

In order to prevent or minimize these flow losses, it is necessary to design the compensation volume 21 in such a way that the energy loss resulting from the additionally occurring flow losses is less than the energy gain achieved by the improved intake. An embodiment of a suction muffler according to the invention shows Fig. 6 , The suction muffler 16 is in Figure 6 shown in sectional view. Fig.1,2 and 3 also show refrigerant compressor with such a suction muffler according to the invention 16. The inlet cross-section 18 of the suction muffler 16 is connected via a schematically illustrated, hermetically sealed connection 19 with connected to the suction tube 17 coming from the evaporator. As a tight connection 19 may in principle any known to those skilled, preferably elastic compound serve, such as a simple rubber hose, but must be tightly connected to the suction muffler 16 and the suction pipe 17. Examples of such compounds show Fig.11 to Fig18 , The suction muffler 16 according to the invention limits a filling volume 20 (the arrangement of a plurality of filling volumes is conceivable and customary). On the suction muffler 16 then a compensation volume 21 is arranged, which is formed by a U-shaped equalization tube 22. The U-shaped compensation tube 22 shown has the advantage of limiting a sufficient compensation volume 21 and, on the other hand, requiring only little additional space, as well as producing the required flow conditions which minimize the mentioned losses. The compensating volume 21 or the compensating pipe 22 communicates with the interior of the compressor housing 1 via a compensating opening 23 and via the transition opening 26 with the filling volume 20 of the suction silencer 16.

Fig. 6 shows the flow of the refrigerant with the intake valve closed, that is located behind the suction port 24 of the suction muffler 16 on the piston side facing the valve plate, by means of arrows.

The cold refrigerant flowing out of the suction pipe 17 flows via the tight connection 19 into the suction silencer volume 20 and further into the compensating volume 21, whereby the warmer refrigerant located there is forced out of the balancing pipe 22 into the interior of the compressor housing 1 via the compensation opening 23. The line marked 25 symbolizes the boundary layer that forms between cold and warm refrigerant.

Figure 7 shows the same suction muffler 16 according to the invention along with the course of flow when the intake valve is open. In this case, the refrigerant is sucked in both from the equalizing volume 21 and from the filling volume 20 and the suction pipe 17. Since the refrigerant in the compensating volume 21 has a lower temperature than the warm refrigerant located inside the compressor housing 1, the mixing temperature of the refrigerants from the mentioned intake ranges is lower than the mixing temperature of the refrigerants when using suction mufflers known from the prior art, whereby mentioned above, unwanted temperature increase is prevented. Warm refrigerant can, due to the feature according to the invention that the compensating volume 21 is 0.5 to 3 times the stroke volume of the piston of the piston-cylinder unit is not from the interior of the compressor housing in the suction muffler, in the embodiment in the volume 20 reach. Due to the fact that the smallest flow cross-section 32 in the compensating volume 21 has a cross-sectional area corresponding to 1/4 to 3/4 of the cross-sectional area of the suction port 24 ensures that the pressure difference between the suction muffler 16 and the interior of the compressor housing 1 is low and at the same time the noise attenuation in the interior of the compressor housing is large. This also contributes to an enlargement of the compensating volume, wherein this is at least half, preferably 0.5 to 3 times the stroke volume of the piston of the piston-cylinder unit.

At the same time, the flow losses are minimized by the suction muffler according to the invention and the refrigerant can flow without problems into the compensating volume 21 or out of it without negatively influencing the refrigerant process.

Figure 8 shows, for the sake of clarity, an oblique view of the suction muffler 16 according to the invention in the compressor housing 1 without piston-cylinder engine unit.

Figure 9 shows an alternative embodiment of a suction muffler 16 according to the invention including compensating volume 21. The compensating volume 21 and the suction muffler 16 are formed by a jacket tube 34 which on the one hand surrounds the suction port 24 and opens into this and on the other hand, an end portion

Suction tube 17 encloses along a section. The cold refrigerant flowing out of the suction pipe 17 flows into the section of the jacket tube 34 forming the filling volume 20 of the suction muffler 16 during the suction cycle. In the subsequent compression cycle, the filling volume 20 of the suction muffler 16 can no longer receive any further refrigerant from the suction pipe 17 due to the closed suction valve Therefore, the refrigerant flows back into the compensating volume 21, which is likewise formed by a section of the jacket tube 34, and displaces the warm refrigerant contained therein via the compensation opening 23 into the interior of the compressor housing 1.

Again, it comes as in Fig. 5 and 6 described to form a movable depending on the Ansaugzyklus boundary layer 25 between hot and cold refrigerant. During the next intake cycle, cold refrigerant can be sucked into the cylinder both from the intake manifold 17 and from the compensation volume 21 of the shroud tube 34. It is important that the boundary layer the designated 33 line, which in this embodiment simultaneously the inlet cross section 18 in the suction muffler 16 and the Transition opening 26 forms, not in the direction of suction port 24 is exceeded to prevent mixing of hot and cold refrigerant before the intake process.

At the same time no cold refrigerant from the suction pipe 17 may be forced out of the compensating volume 21 in the compressor housing 1, the boundary layer 25 thus not behind the in Figure 9 with 23 (compensation opening) marked line to be moved. Regardless of the embodiment, therefore, the invention described exact coordination of the volume of the compensation volume 21 to the cooling capacity and thus to the displacement of the piston-cylinder unit is required.

9a shows a further alternative embodiment of a Saugschalldämpfers 16 including compensating volume 21, wherein the suction muffler 16 compared to that from Figure 9 still has an additional volume 20. Otherwise, this variant is with those in Figure 9 shown identical.

Figure 10 shows an additional alternative embodiment of a suction muffler 16 according to the invention. The reference numerals have been maintained accordingly. As can be seen due to the large number of different designs, the design of the compensation volume is in principle freely selectable as long as the features according to the invention of the compensation volume 21, which is located upstream of the outlet opening of the suction tube 17, regarding its volume and the smallest flow cross-section 32 are maintained. Only then can optimal energy savings be achieved and the efficiency of the refrigerant compressor be improved accordingly.

As the different compensation volumes 21 and suction muffler 16 are constructed, as long as the features of the invention are realized as long as the gas column and the boundary layer 25 can oscillate in the compensation volume.

Thus, the suction muffler 16 in the embodiment according to Fig. 9 only from a substantially conically extending volume 20, in the embodiment according to 9a from a substantially conically extending volume 20a and the volume 20 and in the embodiment according to Figure 10 from the volumes V2 and V1. The parallel or serial arrangement of additional volumes of the suction muffler 16 is, of course, always possible and requires improved sound-damping properties of the suction muffler 16.

The compensating volume 21 is in the embodiment according to Figure 9 from a cylindrical volume, in the embodiment according to 9a also from a cylindrical volume and in the embodiment according to Figure 10 from the volume 21a and 21b. The further arrangement of equalization volumes, parallel or serial, is of course possible, these, such as 21b contribute to the sound attenuation. The smallest flow cross-section 32 according to the invention can either by a diaphragm as in Figure 9 . 9a and 10 shown, realized or by a spatial constriction as in Figure 3 seen. Alternatively, of course, the entire compensating volume 21 can have a constant cross section with the features according to the invention.

The FIGS. 11 to 18 Only if this connection is actually tight, in other words, if no warm refrigerant from the compressor housing 1 is sucked into the suction muffler 16, the compensating volume 21 unfolds its optimal effect , provided it is a variant as in Fig.6 and Fig.7 described.

The easiest connection shows Figure 11 , In this case, the elastic bellows 19 is slipped over the suction tube 17, without further fixation, but preferably glued.

FIGS. 12 and 13 show a more complex but also more stable connection.

In Figure 12 For example, the wall of the compressor housing 1 has an inwardly directed extension 28 over which the elastic plastic hose 19 is slipped, which simultaneously protrudes into the inlet cross section 18 of the suction muffler 16. The plastic tube 19, which may also be designed as an elastic tube is surrounded by a coil spring 27, which provides the necessary stability and fixation. Both in the region of the extension 28 and in the region of the inlet cross section 18, in each case an O-ring 29 is arranged, which is responsible for the required tightness.

In Figure 13 Also, the suction muffler 16 has a correspondingly directed into the interior of the compressor housing 1 extension.

The Fig.14 to 18 show different mounting options 30 between elastic connecting means 19 and suction tube 17, which can be designed either as a toothing ( Fig.17, Fig.18 ) or as arranged on the elastic connecting means barbs ( Figure 16 ) or as simple paragraphs ( Fig.14, Fig.15 ).

In a variant of the compensating volume 21 together with the suction muffler 1 as in Figure 9 . 9a and 10 described omitted the need for such a tight connection between suction muffler 16 and suction pipe 17 for the reasons described.

Fig.19, Fig.20 . Fig.21, and Fig.22 show a further embodiment of a suction muffler 16 together Equalization volume 21 as in the Figure 9 . 9a and 10 already described schematically. The suction tube 17 is thereby brought close to the inlet cross section 18 of the suction muffler 16. The inlet cross-section 18 is connected by means of plastic hose 19 tightly connected to the suction pipe 17.

For clarity, were in the Fig.19, Fig.20 . Fig.21, and Fig.22 the remaining parts of the refrigerant compressor not drawn.

Claims (14)

1. A hermetically encapsulated refrigerant compressor, comprising a hermetically sealed compressor housing (1), in the interior of which a piston-cylinder unit works which compresses a refrigerant and comprises an intake valve with an intake opening (24) arranged in a valve plate of the same, with a muffler (16) being provided on the cylinder head (15) of the piston-cylinder unit, which muffler comprises a filling volume (20) and through which the refrigerant flows to the intake valve of the piston-cylinder unit, and with the muffler (16) having an inlet cross section (18) through which refrigerant flows into the muffler (16) and with a compensating volume (21) being provided which is in connection with the muffler (16) and the interior of the compressor housing (1) and in which the refrigerant oscillates, characterized in that the compensating volume (21) is 0.5 to 3 times the displacement of the piston of the piston-cylinder unit.
2. A hermetically encapsulated refrigerant compressor according to claim 1, characterized in that the smallest flow cross section (32) in the compensating volume (21) has a cross-sectional surface area which corresponds to ¼ to ¾ of the cross-sectional surface area of the intake opening (24).
3. A hermetically encapsulated refrigerant compressor according to one of the claims 1 and 2, characterized in that the cross-sectional surface area of the compensating volume (21) is at most 1.5 times the piston head surface area of the piston of the piston-cylinder unit.
4. A hermetically encapsulated refrigerant compressor according to one of the claims 1 to 3, characterized in that the compensating volume (21) has a circular cross section and the ratio of the length of the compensating volume (21) to its diameter is higher than 10.
5. A hermetically encapsulated refrigerant compressor according to one of the claims 1 to 4, characterized in that the compensating volume (21) is formed by a compensating pipe (22) which has a substantially U-shaped cross section and wraps around the muffler (16) at least partly.
6. A hermetically encapsulated refrigerant compressor according to one of the claims 1 to 5, characterized in that the connection of the inlet cross section (18) of the muffler (16) with the suction pipe (17) is an elastic plastic hose (19) made of PTFE, acrylonitrile, butadiene or fluorinated rubber.
7. A hermetically encapsulated refrigerant compressor according to claim 6, characterized in that the elastic plastic hose is a bellows.
8. A hermetically encapsulated refrigerant compressor according to one of the claims 1 to 7, characterized in that the suction pipe (17) is provided with barbs.
9. A hermetically encapsulated refrigerant compressor according to one of the claims 1 to 8, characterized in that the suction pipe (17) is provided with latching elements which cooperate with respective latching elements on the plastic hose (19).
10. A hermetically encapsulated refrigerant compressor according to one of the claims 1 to 9, characterized in that the inlet cross section (18) and the connecting opening (26) between compensating volume (21) and filling volume (20) are arranged in different sections of the muffler housing.
11. A hermetically encapsulated refrigerant compressor according to one of the claims 1 to 3, characterized in that the inlet cross section (18) is simultaneously the connecting opening (26) between compensating volume (21) and filling volume (20).
12. A hermetically encapsulated refrigerant compressor according to claim 11, characterized in that the compensating volume (21) is formed by an encasing pipe (34) which tightly encloses the intake opening (24) and the inlet cross section (18) respectively on the one hand and encloses the suction pipe (17) of the refrigerant at least along a section and faces into the compressor housing (1) on the other hand, which suction pipe is connected with the evaporator of the refrigerant compressor and protrudes into the interior of the compressor housing (1).
13. A hermetically encapsulated refrigerant compressor according to claim 12, characterized in that the suction pipe (17) is guided close to the intake opening (24) in the encasing pipe (34).
14. A hermetically encapsulated refrigerant compressor according to claim 12 and 13, characterized in that the encasing pipe (34) and the muffler (16) have an integral configuration.

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