Refrigerant compressor

Abstract

Refrigerant compressor, in particular for a refrigeration system, comprising an overall housing (12), a compressor unit (16) arranged in the overall housing (12), a mechanical compressor drive unit (32) for the compressor unit (16) arranged in a drive chamber (34) of the overall housing (12), a lubricant bath (48) forming in the drive chamber (34), an inlet channel (84) extending separately from the drive chamber (34) in the overall housing (12), through which the compressor unit (16) draws in refrigerant to be compressed, wherein the inlet channel (84) and the drive chamber (34) are connected via a gas equalization channel (112) allowing permanent gas equalization between them, characterized in that the refrigerant compressor has a lubricant return (106) which supplies lubricant from a lubricant accumulation (102) forming in the inlet channel (84) to the drive chamber (34),and which prevents lubricant transport from the drive chamber (34) into the inlet channel (84), that the gas equalization channel (112) has, on the one hand, a drive chamber-side opening (114) and, on the other hand, an inlet-side opening (116), and that its channel length (L) between the openings (114, 116) corresponds to at least twice an equivalent channel diameter (AD), and that the drive chamber-side opening (114) of the gas equalization channel (112) is located higher in the direction of gravity than the lubricant bath (48) in the drive chamber (34), and that the gas equalization channel (112) is formed by a pipe that is inserted into a partition (72) between the drive chamber (34) and the inlet channel (84) and that extends from the partition (72) into the drive chamber (34).

Description

[0001] The invention relates to a refrigerant compressor, in particular for a refrigeration system, comprising an overall housing, a compressor unit arranged in the overall housing, a mechanical compressor drive unit for the compressor unit arranged in a drive chamber of the overall housing, a lubricant bath forming in the drive chamber, an inlet channel running separately from the drive chamber in the overall housing, through which the compressor unit draws in refrigerant to be compressed.

[0002] Such refrigerant compressors are known from US 3 033 009 A, which also has gas equalization channels to other compressors and a gas equalization nozzle to the intake channel, and an opening of the gas equalization nozzle on the drive chamber side is located higher in the direction of gravity than the lubricant bath of the drive chamber.

[0003] The general problem with these is that a significant lubricant throw occurs on the outlet side of the compressor, meaning a significant proportion of lubricant in the compressed refrigerant, which is undesirable.

[0004] The invention is therefore based on the objective of creating a refrigerant compressor in which lubricant throw is reduced as much as possible.

[0005] This problem is solved according to the invention in a refrigerant compressor of the type described above by the fact that the refrigerant compressor has a lubricant return system which supplies lubricant from a lubricant accumulation forming in the inlet channel to the drive chamber, and which in particular prevents lubricant transport from the drive chamber into the inlet channel, and that the inlet channel and the drive chamber are connected via a gas equalization channel which allows permanent gas equalization between them, which has on the one hand an opening on the drive chamber side and on the other hand an opening on the inlet channel side and whose channel length between the openings corresponds to at least twice an equivalent channel diameter, in particular a smallest equivalent channel diameter, of the gas equalization channel.and that the opening of the gas equalization channel on the drive chamber side is higher in the direction of gravity than the lubricant bath in the drive chamber, and that the gas equalization channel is formed by a pipe that is inserted into a partition wall between the drive chamber and the inlet channel and that extends from the partition wall into the drive chamber.

[0006] The advantage of this solution lies in the fact that, on the one hand, the refrigerant compressor operates optimally due to the permanent gas equalization via the gas equalization channel, as gas equalization between the drive chamber and the inlet channel always occurs to compensate for pressure variations caused by blow-by flows or other effects, and on the other hand, the length of the gas equalization channel prevents lubricants, especially lubricant droplets, from being transported from the drive chamber-side opening via the inlet-side opening into the inlet channel and leading to increased lubricant jet at the outlet of the refrigerant compressor.

[0007] It is particularly advantageous if the channel length of the gas equalization channel corresponds to at least three times, better at least four times, preferably at least five times and preferably at least six times the equivalent channel diameter.

[0008] An equivalent channel diameter of the gas equalization channel is understood to be the diameter of a circular channel cross-section whose channel cross-sectional area corresponds to the cross-sectional area of ​​the gas equalization channel, if its cross-sectional shape deviates from a circular cross-sectional shape.

[0009] No further details regarding the absolute dimensions of the gas equalization channel were provided in connection with the previous explanation of the individual embodiments.

[0010] As an alternative or supplement to the solutions described above, a particularly advantageous solution is provided that the gas equalization channel has a channel length of at least 40 mm, better at least 60 mm, even better at least 80 mm, preferably at least 100 mm and preferably at least 110 mm.

[0011] No further details have yet been provided regarding the cross-sectional area of ​​the gas equalization channel.

[0012] As an alternative or supplement to the solutions described above, it is particularly advantageous if the gas equalization channel has a channel cross-sectional area of ​​at least 80 mm². 2 , preferably at least 120 mm 2 , or even better, at least 180 mm 2 , preferably at least 250 mm 2 and especially preferably at least 300 mm 2 This is because such a minimum cross-sectional area improves gas equalization, particularly due to the lower disturbance losses.

[0013] Furthermore, it is particularly advantageous if the drive-side opening of the gas equalization channel is arranged in the direction of gravity at least at the level of a drive shaft of the compressor drive unit.

[0014] It is particularly advantageous if the drive-side opening of the gas equalization channel is located laterally next to the compressor drive unit in the drive room.

[0015] Furthermore, it is preferably provided that the inlet-side opening of the gas equalization channel is located higher in the direction of gravity than the lubricant accumulation in the inlet channel.

[0016] Furthermore, if the inlet channel and the drive chamber are separated from each other by a separating element, in particular a partition wall of the overall housing, it is preferably provided that the gas equalization channel passes through a separating element between the drive chamber and the inlet channel.

[0017] An optimal spatial arrangement of the gas equalization channel is achieved when the gas equalization channel extends at least half of its channel length in or along the drive space.

[0018] The function of the gas equalization channel is particularly optimal when, during gas equalization in the gas equalization channel, a column of gas located between the openings moves back and forth in the gas equalization channel without flowing through the gas equalization channel, i.e., that the gas column does not completely penetrate the entire gas equalization channel but remains in the gas equalization channel to at least a significant extent, i.e., for example, at least one third of its length.

[0019] Another optimal solution provides that a column of gas located between the openings moves back and forth in the gas equalization channel during the suction gas pulsations occurring in the intake channel, so that it does not cause any transport of lubricant droplets from the drive chamber into the intake channel.

[0020] Furthermore, in an optimally effective gas equalization channel, it is provided that a gas column lying in the gas channel between the openings moves back and forth in the gas equalization channel during the suction gas pulsations in the inlet channel only in such a way that lubricant droplets present at the drive chamber-side opening enter the gas equalization channel at most, but do not escape from its inlet-side opening.

[0021] No further details regarding the arrangement of the gas equalization channel have been provided in connection with the previous explanation of the invention.

[0022] The gas equalization channel can have any shape, for example straight, curved or bent, as long as the channel length and cross-sectional area meet the conditions mentioned above.

[0023] For example, the gas equalization channel could be located on an outside of the overall housing.

[0024] However, it is particularly advantageous if the gas equalization channel is located within the overall housing.

[0025] The gas equalization channel can be formed by a separate part arranged within the overall housing, which is held, for example, on a housing wall, or it can be designed as a channel integrated into the overall housing.

[0026] Furthermore, it is advantageously provided that the gas equalization channel connects only the intake channel running within the overall housing to the engine compartment, but does not extend, for example, to cylinder heads mounted on the overall housing or into the intake chambers of these cylinder heads. A particularly simple and therefore advantageous design solution provides that the intake channel passes through an engine compartment within the overall housing and that the lubricant collects at the bottom of this engine compartment.

[0027] In this case, it is particularly advantageous from a design perspective if the gas equalization channel connects the drive compartment with the engine compartment.

[0028] In particular, when lubricant is deposited in the inlet channel, a lubricant return system is provided, which supplies lubricant from a lubricant accumulation forming in the inlet channel to the drive chamber, and which in particular prevents lubricant transport from the drive chamber into the inlet channel.

[0029] Furthermore, a particularly advantageous solution regarding lubricant recirculation includes a check valve, which is either directly effective between the inlet channel and the drive chamber or is assigned to a channel running between the inlet channel and the drive chamber, so that the check valve prevents lubricant transport from the drive chamber into the inlet channel.

[0030] The solution described above is particularly advantageous in the case of lubricant recirculation, since the gas equalization channel according to the invention ensures that the lubricant recirculation works optimally and, in particular, that no pressure fluctuations occur due to the lubricant recirculation.

[0031] One particularly advantageous solution involves the refrigerant compressor being a semi-hermetic compressor, in which the inlet channel flows through the engine compartment to cool the drive motor.

[0032] No further details have been provided regarding the compressor unit.

[0033] In principle, the compressor unit could be designed in any way.

[0034] However, a particularly advantageous solution provides for the compressor unit to be designed as a piston compressor unit.

[0035] Furthermore, no specific information was given regarding the compressor drive unit, as its design also depends on the compressor unit.

[0036] One advantageous solution provides that the compressor drive unit includes a drive shaft, in particular a crankshaft, with eccentrics and connecting rods driven by these.

[0037] The foregoing description of solutions according to the invention thus includes in particular the various combinations of features defined by the following numbered embodiments: Refrigerant compressor, in particular for a refrigeration system, comprising an overall housing (12), a compressor unit (16) arranged in the overall housing (12), a mechanical compressor drive unit (32) for the compressor unit (16) arranged in a drive chamber (34) of the overall housing (12), a lubricant bath (48) forming in the drive chamber (34), an inlet channel (84) extending separately from the drive chamber (34) in the overall housing (12), through which the compressor unit (16) draws in refrigerant to be compressed, wherein the inlet channel (84) and the drive chamber (34) are connected via a gas equalization channel (112) which allows permanent gas equalization between them, characterized in that the refrigerant compressor has a lubricant return (106) which supplies lubricant from a lubricant accumulation (102) forming in the inlet channel (84) to the drive chamber (34), and which prevents lubricant transport from the drive chamber (34) into the inlet channel (84), that the gas equalization channel (112) has on the one hand a drive chamber-side opening (114) and on the other hand an inlet-side opening (116) and whose channel length (L) between the openings (114, 116) corresponds to at least twice an equivalent channel diameter (AD), and that the drive chamber-side opening (114) of the gas equalization channel (112) is located higher in the direction of gravity than the lubricant bath (48) in the drive chamber (34) and the gas equalization channel (112) is formed by a pipe,which is inserted into a partition (72) between the drive chamber (34) and the inlet channel (84) and which extends from the partition (72) into the drive chamber (34).

[0038] 2. Refrigerant compressor according to embodiment 1, wherein the channel length (L) of the gas equalization channel (112) corresponds to at least three times, or better yet at least four times, the equivalent channel diameter (AD).

[0039] 3. Refrigerant compressor according to the preamble of embodiment 1 or according to one of the preceding embodiments, wherein the gas equalization channel (112) has a channel length (L) of at least 40 mm, better at least 60 mm, and even better at least 80 mm.

[0040] 4. Refrigerant compressor according to one of the preceding embodiments, wherein the gas equalization channel (112) has a channel cross-sectional area (Q) of at least 80 mm² 2 , preferably at least 120 mm 2, or even better, at least 180 mm 2 amounts.

[0041] 5. Refrigerant compressor according to one of the preceding embodiments, wherein the drive-room-side opening (114) of the gas equalization channel (112) is arranged in the direction of gravity at least at the level of a drive shaft (38) of the compressor drive unit (32).

[0042] 6. Refrigerant compressor according to one of the preceding embodiments, characterized in that the drive-chamber-side opening (114) of the gas equalization channel (112) is arranged laterally next to the compressor drive unit (32) in the drive chamber (34).

[0043] 7. Refrigerant compressor according to one of the preceding embodiments, wherein the inlet channel-side opening (116) of the gas equalization channel (112) is located higher in the direction of gravity than the lubricant accumulation (102) in the inlet channel (84).

[0044] 8. Refrigerant compressor according to one of the preceding embodiments, wherein the gas equalization channel (112) passes through a separating element (72) between the drive chamber (34) and the inlet channel (84).

[0045] 9. Refrigerant compressor according to one of the preceding embodiments, wherein the gas equalization channel (112) extends over at least half of its channel length (L) in or along the drive space (34).

[0046] 10. Refrigerant compressor according to one of the preceding embodiments, wherein during gas equalization in the gas equalization channel (112) a gas column located between the openings (114, 116) moves back and forth in the gas equalization channel (112) without flowing through the gas equalization channel (112), wherein the movements of the gas column are limited due to the large cross-sectional area Q and the large channel length L of the gas equalization channel (112).

[0047] 11. Refrigerant compressor according to one of the preceding embodiments, wherein the gas equalization channel (112) is designed such that a gas column located between the openings (114, 116) moves back and forth in the gas equalization channel (112) during the suction gas pulsations occurring in the inlet channel (84) in such a way that it does not cause any transport of lubricant droplets from the drive chamber (34) into the inlet channel (84), wherein the movements of the gas column are limited due to the large cross-sectional area Q and the large channel length L of the gas equalization channel (112).

[0048] 12. Refrigerant compressor according to one of the preceding embodiments, wherein the gas equalization channel (112) is designed such that a gas column located in the gas equalization channel (112) between the openings (114, 116) moves back and forth in the gas equalization channel (112) during the suction gas pulsations in the inlet channel (84) only such that lubricant droplets present at the drive-side opening (114) enter the gas equalization channel (112) to a maximum extent, but do not exit from its inlet-side opening (116), wherein the movements of the gas column are limited due to the large cross-sectional area Q and the large channel length L of the gas equalization channel (112).

[0049] 13. Refrigerant compressor according to one of the preceding embodiments, wherein the inlet channel (84) penetrates a motor compartment (54) in the overall housing (12) and the lubricant accumulation (102) forms on the bottom side of the motor compartment (54).

[0050] 14. Refrigerant compressor according to embodiment 13, wherein the gas equalization channel (112) connects the drive compartment (34) with the motor compartment (54).

[0051] 15. Refrigerant compressor according to one of the preceding claims, characterized in that a lubricant return (106) comprises a check valve.

[0052] 16. Refrigerant compressor according to one of the preceding embodiments, wherein the refrigerant compressor is a semi-hermetic compressor in which the inlet channel (84) flows through the motor compartment (54) for cooling a drive motor (56).

[0053] 17. Refrigerant compressor according to one of the preceding embodiments, wherein the compressor unit (16) is designed as a piston compressor unit.

[0054] 18. Refrigerant compressor according to one of the preceding embodiments, wherein the compressor drive unit (32) comprises a drive shaft (38) with eccentrics (42) and connecting rods (44) driven by these.

[0055] Further features and advantages of the invention are the subject of the following description and the graphic representation of an exemplary embodiment.

[0056] The drawing shows: Fig. 1 a side view of an embodiment of a refrigerant compressor according to the invention; Fig. 2 a cut along line 2-2 in Fig. 1; Fig. 3 a cut along line 3-3 in Fig. 2; Fig. 4 a cut along line 4-4 in Fig. 2; Fig. 5 a cut along line 5-5 in Fig. 2; Fig. 6 an enlarged partial section of an area comprising a gas equalization channel in Fig. 5; Fig. 7 a cut similar Fig. 3 by a second embodiment of a refrigerant compressor according to the invention and Fig. 8 a cut similar to Fig. 3 by a third embodiment of a refrigerant compressor according to the invention.

[0057] A in Fig. Figure 1, an embodiment of a refrigerant compressor 10 according to the invention for a refrigeration system not shown in the drawing, comprises a total housing 12, which has a compressor section 14 in which, for example, a Fig. 2 to Fig. 4 compressor unit 16 is arranged, which in the illustrated embodiment has at least one, preferably several cylinder bores 22 with pistons 24 movable in these, wherein the cylinder bores 22 are each closed, for example, by a valve plate 26 placed on top, on which cylinder heads 28 are arranged on a side opposite the cylinder bores 22, which are mounted on the overall housing 12.

[0058] The individual pistons 24 of the compressor unit 16 are driven by a mechanical compressor drive unit 32, which is arranged in a drive chamber 34 of the compressor section 14 and which, for example, comprises a drive shaft 38 rotatable about an axis 36, which is provided with eccentrics 42 which in turn are coupled to the pistons 24 by means of connecting rods 44 in order to move them in the cylinder bores 22.

[0059] Furthermore, a lubricant bath 48 forms in a bottom area 46 of the drive chamber 34 that lies lowest in the direction of gravity, in which lubricant for the lubrication of the compressor unit 16 and the compressor drive unit 32 collects, which is supplied to both the compressor unit 16 and the compressor drive unit 32 for lubrication via conveying elements not shown, for example pump elements.

[0060] The overall housing 12 further comprises a motor section 52 arranged in the direction of the axis 36 following the compressor section 14, which encloses a motor compartment 54 in which a motor 56, in particular an electric drive motor, is arranged, the stator 62 of which is fixedly arranged in the motor section 52, while the rotor 64 sits on a rotor shaft 66 which preferably runs coaxially to the drive shaft 38 and is in particular integrally connected to it and is thus also rotatable about the axis 36 in order to drive the drive shaft 38 of the compressor drive unit 32.

[0061] In the overall housing 12, the drive compartment 34 and the motor compartment 54 are separated from each other by separating elements, for example by a partition 72, which preferably carries a bearing unit for the drive shaft 38 and the rotor shaft 66.

[0062] Preferably, the bearing unit 74 forms a bearing sleeve 76 molded onto the partition wall 72.

[0063] In the illustrated embodiment, an inlet port 82 is provided in the area of ​​the engine section 52 for the refrigerant to be compressed by the refrigerant compressor 10, through which the refrigerant enters an inlet channel of the overall housing 12, designated as a whole by 84, which runs through the engine compartment 54 to the partition 72 and, following the partition 72, transitions into a distributor 86 running in the compressor section 14, from which the refrigerant to be compressed then enters inlet chambers of the cylinder heads 28, is compressed by the compressor unit 16 and, as compressed refrigerant, is supplied to outlet chambers of the cylinder heads 28, from which it enters an outlet channel 94 in the housing section 14 and is led from there to an outlet port 96.

[0064] In the inlet channel 84, particularly in the area of ​​the engine compartment 54, lubricant typically accumulates in such refrigerant compressors. This lubricant results from lubricant separated from the aspirated refrigerant and lubricant escaping from the bearing unit 74, forming a lubricant accumulation 102 in the area of ​​the lowest point 104 of the inlet channel 84, particularly in the engine compartment 54. This lubricant should be removed from the inlet channel 84 to reduce lubricant jet at the outlet port 96 of the refrigerant compressor 10.

[0065] For this purpose, a lubricant return is provided in the partition 72 between the inlet channel 84, in particular the engine compartment 54, and the drive compartment 34, which supplies lubricant from the lubricant accumulation 102 to the drive compartment 34.

[0066] It is advantageous to prevent a backflow of lubricant into the inlet channel 84. To achieve this, a check valve 106 is provided, which allows only the passage of lubricant from the lubricant reservoir 102 in the inlet channel 84 into the lubricant bath 48.

[0067] To achieve this, the pressure differences occurring between the inlet channel 84 and the drive chamber 34 when the refrigerant compressor is running are used to act on the lubricant accumulation 102 and cause it to pass through the check valve 106 into the lubricant bath 48.

[0068] However, these pressure differences cause a pumping effect on the lubricant accumulation 102, especially when, in addition to the check valve 106, gas equalization takes place between the drive chamber 34 and the inlet channel 84.

[0069] To compensate for any kind of pressure difference between the drive chamber 34 and the inlet channel 84, for example caused by blow-by flows from the compressor unit 16 or suction gas pulsations or other effects, a [component] is provided. Fig. 2, Fig. 3 and Fig. 5 Gas equalization channel 112 is provided, which penetrates the partition wall 72 and enables the aforementioned gas equalization between the drive compartment 34 and the inlet channel 84, in particular in this case the engine compartment 54.

[0070] The gas equalization channel 112 is routed in such a way that, as in Fig. 2 shown, a buoyancy chamber-side opening 114 of the same in the drive chamber 34 is located at a sufficient distance from a surface 118 of the lubricant bath 48 in the drive chamber 34 and an inlet channel-side opening 116 of the gas equalization channel 112 is also located at a sufficient height above the lubricant accumulation 102 in the inlet channel 84, in particular in the engine compartment 54.

[0071] Preferably, the gas equalization channel 112 is formed by a pipe 118 which is inserted into and held by the partition wall 72, wherein the pipe 118 preferably extends from the partition wall 72 into the drive chamber 34.

[0072] To prevent lubricant droplets present in the drive chamber 34 from being transported into the inlet channel 84, and in particular the engine compartment 54, during gas equalization between the drive chamber 34 and the inlet channel 84 and thus also the engine compartment 54, the inlet channel 112 is designed such that it has a channel length L between the drive chamber-side opening 114 and the inlet channel-side opening 116 which is at least 40 mm, better at least 60 mm, preferably at least 80 mm and most preferably at least 100 mm or better at least 110 mm.

[0073] Furthermore, it is preferably provided that the gas equalization channel 112 has a channel cross-sectional area Q of at least 80 mm² 2 , better 120 mm 2 , or even better, at least 180 mm 2 preferably at least 250 mm 2 or, even more advantageously, at least 300 mm 2amounts.

[0074] In particular, it is provided that the channel length L of the gas equalization channel 112 corresponds to at least twice, better at least three times, even better at least four times, preferably at least five times and preferably at least six times the equivalent channel diameter AD, wherein the equivalent channel diameter AD corresponds to the diameter of a gas equalization channel 112 with a circular cross-section or, in the case of a gas equalization channel 112 with a cross-sectional shape deviating from a circular cross-section, corresponds to the channel diameter of a channel cross-sectional area Q with a circular cross-section, which is equal to the channel cross-sectional area Q' of the gas equalization channel 112 with a different cross-sectional shape.

[0075] Such dimensions of the gas equalization channel 112 make it possible that essentially no lubricant transport, in particular no transport of lubricant droplets, takes place through the gas equalization channel 112 from the drive chamber 34 into the inlet channel 84, in particular the engine chamber 54.

[0076] This is possible because the channel length L and the channel cross-sectional area Q of the gas equalization channel 112 cause a gas column to form in it, which moves back and forth due to the pressure differences 84 between the drive chamber-side opening 114 and the inlet channel-side opening 116, whereby the movements of the gas column are limited due to the large cross-sectional area Q and the large channel length L of the gas equalization channel 112 in such a way that no lubricant droplets are transported from the drive chamber-side opening 114 in the drive chamber 34 to the inlet channel-side opening 116 and escape from it when the gas column moves back and forth.

[0077] Rather, when the gas column moves back and forth in the lubricant channel 112, the lubricant droplets entering through the drive-side opening 114 do not travel as far as the inlet-side opening 116, but only into the gas equalization channel 112 and essentially from there back out to the drive-side opening 114 or only to the extent that they remain in the gas equalization channel 112 and are possibly separated there.

[0078] In particular, the solution according to the invention allows, on the one hand, the lubricant accumulating in the inlet channel 84 and especially in the motor compartment 54 to be fed from the lubricant accumulation 102 via the check valve 106 to the lubricant bath 48 in the drive compartment 34 and, on the other hand, to prevent lubricant droplets from being transported from the drive compartment 34 into the inlet channel 84, especially the motor compartment 54, via the gas equalization channel 112, thus reducing the lubricant throw in such refrigerant compressors, especially when they are operated as transcritical CO2 machines.

[0079] In particular, the gas equalization channel 112 dimensioned and functioning as described above thus allows for an overall significant reduction in lubricant jet at the outlet port 96.

[0080] In a second embodiment of a refrigerant compressor according to the invention, shown in Fig. 7, the gas equalization channel 112' is designed to slope downwards in the direction of the drive chamber 34, such that its inlet channel-side opening 116' is higher in the direction of gravity than the drive chamber-side opening 114', so that in the event that lubricant settles in the gas equalization channel 112', it escapes from the drive chamber-side opening 114' due to the effect of gravity and collects in the lubricant bath 48.

[0081] This also ensures that no lubricant settling in the gas equalization channel 112' unintentionally enters the inlet channel 84.

[0082] In a third embodiment of a refrigerant compressor according to the invention, shown in Fig.8, the gas equalization channel 112" is designed such that it has a lowest point 122 between the drive chamber-side opening 114" and the inlet channel-side opening 116" in which lubricant collects that is deposited in the gas equalization channel 112".

[0083] Furthermore, the lowest point 122 is also assigned a drip opening 124 which is smaller in relation to the channel cross-sectional area Q, in particular by a factor of 10, which allows the lubricant collecting in the lowest point 122 to escape from the gas equalization channel 112" and - if necessary by means of an additional line - be supplied to the lubricant bath 48 by the effect of gravity.

[0084] Such a lowest point 122 in the direction of gravity can be achieved, for example, by having the gas equalization channel 112" have a downward deflection in the direction of gravity, preferably located in the drive chamber 34, so that the lubricant exiting the drip opening is supplied to the lubricant bath 48 without a further line.

Claims

[1] Refrigerant compressor, in particular for a refrigeration system, comprising an overall housing (12), a compressor unit (16) arranged in the overall housing (12), a mechanical compressor drive unit (32) for the compressor unit (16) arranged in a drive chamber (34) of the overall housing (12), a lubricant bath (48) forming in the drive chamber (34), an inlet channel (84) extending separately from the drive chamber (34) in the overall housing (12), through which the compressor unit (16) draws in refrigerant to be compressed, wherein the inlet channel (84) and the drive chamber (34) are connected via a gas equalization channel (112) which allows a permanent gas equalization between them, characterized by, that the refrigerant compressor has a lubricant return system (106) which supplies lubricant from a lubricant accumulation (102) forming in the inlet channel (84) to the drive chamber (34), and which prevents lubricant transport from the drive chamber (34) into the inlet channel (84), that the gas equalization channel (112) has on the one hand a drive chamber-side opening (114) and on the other hand an inlet-side opening (116) and whose channel length (L) between the openings (114, 116) corresponds to at least twice an equivalent channel diameter (AD), and that the drive chamber-side opening (114) of the gas equalization channel (112) is located higher in the direction of gravity than the lubricant bath (48) in the drive chamber (34) and the gas equalization channel (112) is formed by a pipe,which is inserted into a partition (72) between the drive chamber (34) and the inlet channel (84) and which extends from the partition (72) into the drive chamber (34). [2] Refrigerant compressor according to claim 1, characterized by , that the channel length (L) of the gas equalization channel (112) corresponds to at least three times, or better yet at least four times, the equivalent channel diameter (AD). [3] Refrigerant compressor according to the preamble of claim 1 or according to any of the preceding claims, characterized by , that the gas equalization channel (112) has a channel length (L) of at least 40 mm, better at least 60 mm, even better at least 80 mm. [4] Refrigerant compressor according to any of the preceding claims, characterized by , that the gas equalization channel (112) has a channel cross-sectional area (Q) of at least 80 mm 2 , preferably at least 120 mm 2 , or even better, at least 180 mm2 amounts. [5] Refrigerant compressor according to any one of the preceding claims, characterized by , that the drive-side opening (114) of the gas equalization channel (112) is arranged in the direction of gravity at least at the level of a drive shaft (38) of the compressor drive unit (32). [6] Refrigerant compressor according to any one of the preceding claims, characterized by , that the drive-side opening (114) of the gas equalization channel (112) is arranged laterally next to the compressor drive unit (32) in the drive room (34). [7] Refrigerant compressor according to any one of the preceding claims, characterized by , that the inlet channel-side opening (116) of the gas equalization channel (112) is higher in the direction of gravity than the lubricant accumulation (102) in the inlet channel (84). [8] Refrigerant compressor according to any one of the preceding claims, characterized by, that the gas equalization channel (112) passes through a separating element (72) between the drive chamber (34) and the inlet channel (84). [9] Refrigerant compressor according to any one of the preceding claims, characterized by , that the gas equalization channel (112) extends over at least half of its channel length (L) in or along the drive chamber (34). [10] Refrigerant compressor according to any one of the preceding claims, characterized by , that during gas equalization in the gas equalization channel (112) a column of gas located between the openings (114, 116) moves back and forth in the gas equalization channel (112) without flowing through the gas equalization channel (112), the movements of the gas column being limited due to the large cross-sectional area Q and the large channel length L of the gas equalization channel (112). [11] Refrigerant compressor according to any of the preceding claims, characterized by, that the gas equalization channel (112) is designed such that a gas column located between the openings (114, 116) moves back and forth in the gas equalization channel (112) during the suction gas pulsations occurring in the inlet channel (84) in such a way that it does not cause any transport of lubricant droplets from the drive chamber (34) into the inlet channel (84), wherein the movements of the gas column are limited due to the large cross-sectional area Q and the large channel length L of the gas equalization channel (112). [12] Refrigerant compressor according to any one of the preceding claims, characterized by, that the gas equalization channel (112) is designed such that a gas column located in the gas equalization channel (112) between the openings (114, 116) moves back and forth in the gas equalization channel (112) during the suction gas pulsations in the inlet channel (84) only in such a way that lubricant droplets present at the drive chamber-side opening (114) enter the gas equalization channel (112) at most, but do not exit from its inlet-side opening (116), whereby the movements of the gas column are limited due to the large cross-sectional area Q and the large channel length L of the gas equalization channel (112). [13] Refrigerant compressor according to any of the preceding claims, characterized by , that the inlet channel (84) passes through an engine compartment (54) in the overall housing (12) and that the lubricant accumulation (102) forms on the bottom side of the engine compartment (54). [14] Refrigerant compressor according to claim 13, characterized by, that the gas equalization channel (112) connects the drive compartment (34) with the engine compartment (54). [15] Refrigerant compressor according to any one of the preceding claims, characterized by , that a lubricant return (106) includes a check valve. [16] Refrigerant compressor according to any one of the preceding claims, characterized by , that the refrigerant compressor is a semi-hermetic compressor in which the inlet channel (84) flows through the engine compartment (54) to cool a drive motor (56). [17] Refrigerant compressor according to any one of the preceding claims, characterized by , that the compressor unit (16) is designed as a piston compressor unit. [18] Refrigerant compressor according to any one of the preceding claims, characterized by , that the compressor drive unit (32) comprises a drive shaft (38) with eccentrics (42) and connecting rods (44) driven by these.

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