SCROLL MACHINE AND REFRIGERATION SYSTEM

Description

[0001] The present invention relates to a scroll machine, in particular a spiral compressor for a medium, in particular a refrigerant, and to a refrigeration system with such a scroll machine.

[0002] Scroll machines are fluid energy machines and are known in various designs from the prior art. Examples of scroll machines include scroll compressors, scroll compressors or spiral compressors, and scroll expanders.

[0003] Known scroll machines typically feature two cooperating spiral units, each with at least one spiral rib forming at least one spiral channel. The spiral ribs of the spiral units interlock to form pressure chambers, with the spiral ribs sealingly abutting the spiral channel floor of the other spiral unit.

[0004] Both the spiral channel and the spiral rib forming the spiral channel are shaped like a circular involute, with the two spiral units being movable relative to each other. A common design of scroll machines features a stationary spiral unit and a movable spiral unit, the first movable spiral unit moving along an orbital path relative to a second spiral unit.

[0005] In a compressor, a medium, such as a refrigerant, is compressed according to the displacement principle by the relative movement of two spiral units. During this relative movement, the medium is moved along the spiral channels in pressure chambers from an outer end to an inner end, undergoing a change in volume within each pressure chamber.

[0006] In an expander, the medium, especially refrigerant, is expanded by a relative movement of the two spiral units. During this relative movement, the medium is displaced in pressure chambers along the spiral channels from an inner end region to an outer end region, thereby experiencing an increase in volume within each pressure chamber.

[0007] WO 2018 019 372 A1 discloses, for example, such a generic scroll machine that can be used in a refrigeration system with a refrigerant circuit. Such refrigeration systems can be used in a variety of applications, such as cooling a secondary fluid like air or cooling components or equipment. The cooling or heating load of refrigeration systems can vary considerably depending on ambient conditions, occupancy levels, and other load requirements.

[0008] Documents US 2009 / 162222 A1 and US 2004 / 057859 A1 disclose scroll machines with a bearing unit and a spiral unit enclosing a space.

[0009] Further state of the art is represented by the publications DE 38 88 212 T2, US 2020 / 080556 A1, DE 100 63 603 A1, KR 2002 0055130 A and DE 38 88 212 T2.

[0010] In the past, the scroll machines and refrigeration systems described above have proven their worth; however, it has been shown that the components of the scroll machine require both continuous cooling and lubrication in order to achieve the required service life.

[0011] This is where the present invention comes in.

[0012] The object of the present invention is to propose a scrolling machine and a refrigeration system of the type described above, which effectively eliminate the disadvantages known from the prior art. The invention aims to provide a scrolling machine and a refrigeration system that are cooled and lubricated effectively in a simple manner.

[0013] These tasks are solved by a scrolling machine with the features of claim 1 and a refrigeration system with the features of claim 21.

[0014] Further advantageous embodiments of the invention are specified in the dependent claims.

[0015] The scrolling machine according to the invention, comprising the features of claim 1 for a medium, in particular a refrigerant, has a machine housing with a longitudinal axis, an inlet, and an outlet for the medium. Furthermore, in the scrolling machine according to the invention, a drive unit, a drive shaft, a first spiral unit, and a second spiral unit are arranged along the longitudinal axis. The drive shaft is supported on the machine housing by a first bearing unit and a second bearing unit, the axis of rotation of the drive shaft preferably determining the position and orientation of the longitudinal axis. The first bearing unit and the second bearing unit are preferably arranged in opposite end sections of the drive shaft.

[0016] The second bearing unit is located in the end section adjacent to the first spiral unit, and the first bearing unit is located in the opposite end section.

[0017] The first spiral unit has a first spiral channel formed by a first spiral rib, which extends from an inner end region to an outer end region.

[0018] The second spiral unit has a second spiral channel formed by a second spiral rib, extending from an inner end region to an outer end region. The inlet of the scroll machine is in fluid communication with the outer end regions of the first and second spiral units, the outer end regions being referred to as the intake region in connection with this invention. The outlet is in fluid communication with the inner end regions, whereby the medium is guided through the inlet and through the machine housing along several flow paths to the outer end regions and from the inner end regions to the outlet.

[0019] The first spiral unit can be moved by means of the drive shaft through the drive unit along an orbital path relative to the second spiral unit, and the first spiral unit and the second spiral unit interlock to form pressure chambers, with the spiral ribs sealingly abutting a spiral channel floor of the other spiral unit.

[0020] According to one embodiment of the present invention, the drive shaft has a hollow shaft section, wherein one of the flow paths is guided through the hollow shaft section. The hollow shaft section is preferably arranged coaxially to the axis of rotation of the drive shaft and can partially or completely penetrate the drive shaft.

[0021] In this embodiment, the drive shaft can simultaneously serve as a conduit for the medium, enabling space-saving and low-pressure-loss routing of the medium within the machine housing. Furthermore, it allows for cooling of the drive shaft and, in particular, the components of the scroll machine connected to the drive shaft, such as the drive shaft bearings. The proposed solution provides a particularly compact scroll machine with integrated cooling and efficient bearing lubrication.

[0022] It should be noted here that the medium is preferably a refrigerant, wherein the refrigerant comprises a lubricant which can be carried along by the refrigerant.

[0023] A further development of the present invention provides that the hollow shaft section is formed by a blind hole. The blind hole preferably extends from an end face of the drive shaft in the first end section towards the second end section.

[0024] Furthermore, according to the further development, the drive shaft can have at least one radial bore that opens into the hollow shaft section and connects the hollow shaft section to an outer surface of the drive shaft. As a result, the medium can be guided along a flow path through the at least one radial bore. The at least one radial bore makes it possible to direct the medium along the longitudinal axis from the drive shaft to individual components, thereby enabling cooling and / or lubrication of these components by the lubricant carried along with the medium.

[0025] In a further embodiment, a rotor of the drive unit can be arranged between the first bearing unit and the second bearing unit, wherein the drive shaft between the first bearing unit and the rotor and / or the drive shaft between the second bearing unit and the rotor has at least one radial bore. Preferably, at least one radial bore is arranged both between the first bearing unit and the rotor and between the second bearing unit and the rotor. The at least one radial bore between the first bearing unit and the rotor and / or between the second bearing unit and the rotor can contribute to improved cooling of the rotor of the drive unit, wherein preferably the drive shaft has several radial bores around its circumference, which, according to a further preferred embodiment, are arranged circumferentially symmetrically.

[0026] Furthermore, according to a further development of the present invention, it has proven advantageous if the drive unit, or preferably an electric drive, has at least one axial opening and / or at least one axial groove around the drive unit, and if the at least one axial opening and / or the at least one axial groove defines a flow path for the medium. Preferably, the drive unit has several axial openings and / or several axial grooves around its circumference, which are preferably arranged circumferentially symmetrically. The at least one axial opening and / or the at least one axial groove connects opposite end faces of the drive unit or the drive, and extensive cooling of the rotor and / or the stator of the drive can be achieved.The at least one axial opening can be formed, for example, by a motor gap and / or the at least one axial groove can be formed by a channel-shaped free space between the stator and the housing. The at least one axial groove and / or axial opening can be formed in the housing and / or the drive unit.

[0027] According to further development, it has proven advantageous if a flow path between the inlet and the first bearing unit is branched into two parallel flow paths, one of which is guided through the hollow shaft section and the other through the first bearing unit. The first bearing unit comprises a secondary bearing body, preferably a rolling bearing not sealed by seals, through which the other flow path is preferably guided.

[0028] Furthermore, the inlet in the machine housing can be located directly in front of the free end of the drive shaft, preferably being arranged approximately coaxially with the drive shaft along its longitudinal axis. The medium coming from the inlet is split into two parallel flow paths, one through which the medium flows into the first bearing unit and the other through the hollow shaft section of the drive shaft. This allows, in particular, the secondary bearing body of the first bearing unit to be cooled, and the lubricant carried along with the medium can also lubricate the secondary bearing body.

[0029] According to the present invention, the second bearing unit and the first spiral unit enclose a space, wherein at least one of the flow paths is led into the space through the second bearing unit.

[0030] The second bearing unit can comprise a main bearing body and a main bearing housing. At least one of the flow paths can be routed through the main bearing housing and / or through the main bearing body. In other words, the flow paths into the space through the second bearing unit can be routed exclusively through the main bearing housing or the main bearing body, or they can be connected in parallel through the main bearing housing and the main bearing body.

[0031] Preferably, at least one flow path is guided through the main bearing body to cool the main bearing body and to lubricate it with the lubricant carried along by the medium. According to a preferred embodiment, the main bearing body can be an unsealed rolling bearing.

[0032] In a preferred embodiment, the second bearing unit divides the machine housing into a drive section and an intake section. The drive unit is located in the drive section, and the outer end regions of the first and second spiral units are located in the intake section. The inlet opens into an intake section, with the first bearing unit positioned between the intake section and the drive section. The medium is guided along the flow paths from the inlet section through the drive section and through the second bearing unit to the intake section and the outer end regions of the first and second spiral units, respectively.

[0033] According to a further development of the present invention, the drive shaft projects into the space through the second bearing unit, wherein a counterweight rigidly connected to the drive shaft and / or an eccentric drive for the first spiral unit are arranged on the drive shaft within this space. An eccentric drive preferably comprises an eccentric section formed as a driver on the drive shaft, which is coupled to the first spiral unit via an eccentric bearing body. Both the counterweight and the eccentric drive can move together with the drive shaft within the space, thereby "stirring" or "swirling" the medium present in the space and allowing a significant amount of the lubricant carried along with the medium to be separated.

[0034] According to a preferred embodiment, the second bearing unit can be cup- or bell-shaped, with the main bearing body and an axial bearing for the first spiral unit being provided on opposite sides of the second bearing unit along its longitudinal axis. The main bearing body is preferably arranged in the region of a vertex of the bell-shaped second bearing unit, and the axial bearing on the opposite end face.

[0035] According to a preferred embodiment of the present invention, at least two parallel flow paths lead from the inlet into the chamber, one flow path being guided through the main bearing body and the other flow path being guided through at least one inlet opening formed as a perforation in the main bearing housing. The two parallel flow paths reduce pressure loss while simultaneously ensuring sufficient lubrication and / or cooling of the main bearing body.

[0036] Preferably, the main bearing housing has several inlet openings, which are more preferably arranged symmetrically around its circumference. The inlet openings are preferably located in a cylindrical surface of the main bearing housing and, even more preferably, approximately centered along the longitudinal axis between the opposite sides of the second bearing unit.

[0037] The invention provides that the space has at least one outlet opening, and that the outlet opening defines a flow path that connects the space with the outer end regions of the first spiral unit and the second spiral unit or the intake area.

[0038] Furthermore, it has proven advantageous if the at least one outlet opening comprises a first bore section and a second bore section, and if the first bore section and the second bore section are arranged in an L- or T-shape. Preferably, the first bore section and the second bore section are each formed along a straight line that intersects at a common point. Even more preferably, the first bore section is oriented radially with respect to the longitudinal axis, and the second bore section is oriented axially. The first bore section is preferably designed as a through bore and connects an outer surface of the main bearing housing to the space. The second bore section can, for example, be formed by a blind bore.Alternatively, at least one of the two bore sections can be formed in the main bearing housing by a primary forming or forming process.

[0039] Preferably, during the intended use of the scroll machine, an outlet opening can be arranged such that lubricant can drain from the chamber through the outlet opening. For this purpose, an outlet opening is particularly well-placed in the underside of the second bearing unit. Separated lubricant can accumulate in the area of ​​the underside and can then be carried away by the flow through the outlet opening or flow off.

[0040] In a further embodiment of the present invention, the at least one outlet opening can be formed by an axial recess extending from the radial outside to the radial inside, interrupting the axial bearing surface. During movement of the first spiral unit along its orbital path, the at least one axial recess is traversed, thereby providing continuous lubrication and cooling of the axial bearing. The transition between the surface of the axial bearing and the at least one radially oriented axial recess can be provided with transition radii.

[0041] A further development provides that an axial bearing element is arranged between the second bearing unit and the first spiral unit, preferably on axial recesses that extend from the radial outside to the radial inside and interrupt the axial bearing surface. The axial bearing element can preferably be an axial bearing plate.

[0042] Furthermore, it has proven advantageous if the at least one outlet opening is formed by a conduit in the second bearing unit, wherein the conduit preferably comprises a first bore section and a second bore section arranged in an L-shape. Preferably, the first bore section is arranged radially and the second bore section is arranged axially. The first bore section and the second bore section can preferably be machined into the second bearing unit or the main bearing housing, wherein preferably the first bore section completely penetrates the second bearing unit, while the second bore section can be designed as a blind hole. The first bore section thus extends from the space to an outer surface of the second bearing unit or the main bearing housing and is preferably enclosed there by the machine housing or the main bearing housing.A section of the machine housing is sealed. The second bore section intersects the first bore section and opens into the outer end regions of the first spiral unit and the second spiral unit, or into the intake area of ​​the two spiral units.

[0043] According to a preferred embodiment of the present invention, the at least one outlet opening is arranged circumferentially offset from the at least one inlet opening with respect to the longitudinal axis of the space. This offset arrangement of the inlet openings relative to the outlet opening allows the residence time of the medium in the space to be extended, thereby increasing the separation rate of the lubricant carried in the medium.

[0044] A preferred embodiment of the present invention provides that the at least one outlet opening on the side of the second bearing unit facing the first spiral unit is arranged partially or completely within an area that is traversed by the first spiral unit during a complete movement along its orbital path. The at least one outlet opening is thus partially or completely traversed at least once during movement along the orbital path of the first spiral unit, thereby lubricating the axial bearing arranged between the second bearing unit and the first spiral unit.

[0045] Furthermore, it has proven advantageous if the first spiral unit has a recess on the side facing the at least one outlet opening, which is located within a surface that the at least one outlet opening passes over during a complete movement of the first spiral unit along its orbital path. This recess prevents the first spiral unit from coming into direct contact with the at least one outlet opening, thereby preventing damage to the outlet opening and / or to a surface of the axial bearing of the first spiral unit.

[0046] A further development of the present invention provides that at least one ring-pin coupling is provided which prevents a complete rotation of the first spiral unit about the longitudinal axis. Such a ring-pin coupling comprises at least one pair of ring-pin couplings, preferably several pairs of ring-pin couplings, each with a pin that engages in an abutment. The pin can move within the annular abutment in a manner corresponding to the orbital path.

[0047] Preferably, one of the flow paths is guided through the ring-pin coupling, with the respective abutment preferably being formed in the second bearing unit and either completely penetrating the second bearing unit or having a connecting bore that penetrates the second bearing unit so that the flow path from the inlet can be guided through the abutment. The lubricant carried along by the refrigerant can be deposited in the ring-pin coupling for lubrication.

[0048] The at least one connecting bore can guide a flow path from the inlet through the second bearing unit to the intake area. The connecting bore does not necessarily have to pass through a ring-pin coupling pair or its abutment as previously described, but can also pass through the second bearing unit beyond the ring-pin coupling pair.

[0049] The at least one ring-pin coupling pair is arranged in the scroll machine during its intended use such that lubricant can drain from the drive section through the ring-pin coupling towards the intake area. For this purpose, a ring-pin coupling is specifically arranged in the area of ​​a lower surface of the second bearing unit.

[0050] According to a further development of the present invention, the second spiral unit is stationary. Thus, the second spiral unit preferably does not move relative to the first spiral unit and the machine housing during the intended operation of the scroll machine.

[0051] In a further development or according to another aspect of the present invention, a high-pressure chamber can be arranged in the housing. The inner end regions of the first spiral unit and the second spiral unit are connected to the high-pressure chamber via a passage, and the medium can leave the machine housing from the high-pressure chamber through the outlet.

[0052] The high-pressure chamber can be connected to an outlet via a pressure port. The pressure port can be arranged in a plane transverse to the longitudinal axis relative to the outlet and can preferably be located in the pressure chamber along the longitudinal axis on the side opposite the outlet. This offset arrangement between the outlet and the pressure port is intended to ensure that pressure pulsations are reduced and that the medium coming from the outlet cannot flow directly out of the scroll machine through the pressure port.

[0053] The high-pressure chamber can incorporate a backflow region that forces an S-shaped flow path from the inlet to the outlet. This backflow region promotes pulsation damping and reduces pressure fluctuations in the medium discharged through the outlet.

[0054] In a further development, an intermediate floor can be provided between the high-pressure chamber and the second spiral unit, with the intermediate floor, together with the machine housing, enclosing the high-pressure chamber. The intermediate floor absorbs a large part of the pressure load of the high-pressure chamber, thereby subjecting the second spiral unit to lower loads.

[0055] It has also proven advantageous if the backflow area is formed by a recess in the intermediate floor on the side facing the high-pressure chamber and the pressure nozzle, with the pressure nozzle projecting into the high-pressure chamber oriented towards the recess.

[0056] Furthermore, it has proven advantageous if the pressure nozzle is in effective contact with the intermediate floor in a contact area to form the flow area, and that the contact area is arranged on an imaginary connecting line in a plane perpendicular to the longitudinal axis between the pressure nozzle and the passage.

[0057] Further development allows for the provision of a check valve located between the high-pressure chamber and the outlet. The check valve can be located either in the outlet or in the pressure port, with the check valve being preferably inserted into the pressure port in the form of a bushing. This results in a particularly compact and simple design.

[0058] Another aspect of the present invention relates to a refrigeration system with a scroll machine described above.

[0059] Two embodiments of the present invention are described in detail below with reference to the accompanying figures. The figures show: Figure 1 is a highly simplified and schematic representation of a refrigeration system with a scroll machine according to the invention; Figure 2 is an enlarged, simplified sectional view of a first embodiment of the scroll machine according to the invention. Figure 1Figure 3 shows an enlarged detail view of the scrolling machine according to Figure 2 Figure 4 shows an enlarged, simplified sectional view of the scrolling machine according to Figure 1 Figure 5 shows a sectional view of the scrolling machine along the section line B - B in Figure 4 , and Figure 6, a sectional view of the scrolling machine along section line A - A in Figure 2 .

[0060] Identical or functionally equivalent parts or features are identified by the same reference numerals in the detailed description of the figures below. Furthermore, not all identical or functionally equivalent parts or features in the figures are assigned a reference number.

[0061] Figure 1 shows a preferred embodiment of a refrigeration system 1 with a scroll machine. 2. The refrigeration system 1 comprises the scroll compressor 2, a condenser 3, an expansion device 4 and an evaporator. 5.A medium, preferably a refrigerant, flows through the refrigeration system 1 along the direction indicated by arrows, first from an outlet 12 of the scroll machine 2 in the sequence to the condenser 3, the expansion element 4, the evaporator 5 and finally back through an inlet 11 into the scroll machine. 2.

[0062] Based on the Figures 2 to 5 A preferred embodiment of the [designation] is described below. Figure 1 The scrolling machine 2 shown is described.

[0063] Figure 2 is a simplified cross-sectional view of the scrolling machine 2 according to Figure 1 The scroll machine 2 has a machine housing 10, referred to as a whole, which is oriented along a longitudinal axis X. The machine housing 10 can have several housing parts, wherein in the present embodiment the machine housing 10 has a first housing part 10' and a second housing part 10''.

[0064] In the machine housing 10, along the longitudinal axis X, according to Figure 2 From right to left the inlet 11, a drive unit 400, a drive shaft 420, a first spiral unit 100, a second spiral unit 200, an intermediate floor 50, a high pressure chamber 30 and the outlet 12 are arranged.

[0065] The first spiral unit 100 is coupled to the drive unit 400 via an eccentric drive 150 and the drive shaft 420.

[0066] The drive unit 400 preferably comprises an electric drive with a rotor 410 and a stator 415, wherein the rotor 410 is rigidly coupled to the drive shaft 420.

[0067] The drive shaft 420 is aligned in the longitudinal axis X and the axis of rotation of the drive shaft 420 defines the longitudinal axis in the illustrated embodiment. X.The drive shaft 420 has a first end section and a second end section on opposite sides in the longitudinal axis X.

[0068] In the first end section, the drive shaft 420 is supported on the machine housing 10 by a first bearing unit 450, and in the second end section by a second bearing unit 300. The rotor 410 of the drive unit 400 is arranged between the first bearing unit 450 and the second bearing unit 300.

[0069] The drive shaft 420 has a hollow shaft section 424 oriented along the longitudinal axis X. The hollow shaft section 424 can be configured as a blind bore and extends from a free end face of the drive shaft 420 in the first end section towards the second end section.

[0070] The drive shaft 420 also includes several radial bores 428 that penetrate the drive shaft 420 and connect the hollow shaft section 424 with an outer cylindrical surface of the drive shaft 420.

[0071] According to Figure 2 The drive shaft 420 can have at least one radial bore 428 between the first bearing unit 450 and the rotor 410 and / or between the second bearing unit 300 and the rotor 410. In the preferred embodiment shown, the drive shaft 420 has two radial bores 428 between the first bearing unit 450 and the rotor 410 and between the second bearing unit 300 and the rotor 410, which are arranged circumferentially symmetrically to the drive shaft 420.

[0072] The first bearing unit 450 comprises a bearing receptacle 452 and a secondary bearing body 455. The bearing receptacle 452 can be formed by the machine housing 10. The secondary bearing body 455 can be designed as a rolling bearing, which is preferably not sealed.

[0073] The first bearing unit 450 divides the interior of the machine housing 10 into an inlet section and a drive section, with the inlet 11 opening into the inlet section.

[0074] The inlet 11 is preferably arranged on an end face of the machine housing 10, wherein the inlet 11 is even more preferably arranged in line with the drive shaft 420 - preferably directly in front of the free end face of the drive shaft 420.

[0075] The second bearing unit 300 comprises a main bearing housing 302 and a main bearing body 305. The main bearing body 305 can be designed as a rolling bearing, preferably unsealed. The second bearing unit 300 further divides the interior of the machine housing 10 into the drive section and an intake area 320.

[0076] The second bearing unit 300 has a first side and a second side, the first side facing the drive unit 400 and the second side facing the first spiral unit 100. The main bearing body 305 is arranged on the first side and an end face on the second side forms an axial bearing 190 for the first spiral unit 100.

[0077] The second bearing unit 300 or the main bearing housing 302 can be bell- or pot-shaped and enclose a space 380 together with the first spiral unit 100.

[0078] The chamber 380 has several inlet openings 370, which are formed in the second bearing unit 300 and in the main bearing housing 302, respectively. The inlet openings 370 penetrate the main bearing housing 302 and open into the chamber 380. For example, the second bearing unit 300 can have four inlet openings 370, as shown in Figure 5 As shown, they can be arranged circumferentially symmetrically on a lateral surface, preferably approximately midway between the first side and the second side.

[0079] Furthermore, the space 380 can have several outlet openings 390, which are preferably formed in the second bearing unit 300 or the main bearing housing 302. Figure 3 shows an enlarged detail view according to Figure 2 which shows that the outlet opening 390 can be formed from a first bore section 392 and a second bore section 394 in the main bearing housing 302.

[0080] The first bore section 392 is essentially radially oriented and extends from the space 380. For manufacturing reasons, it may be advantageous if the first bore section 392 completely penetrates the main bearing housing 302.

[0081] The second bore section 394 is essentially axially oriented and connects the second side of the second bearing unit 300 or the main bearing housing 302 with the first bore section 392.

[0082] The second bearing unit 300 can have four outlet openings 390, which are preferably arranged circumferentially symmetrically. Furthermore, the outlet openings 390 can be oriented relative to the inlet openings 370 – as in Figure 5 indicated - arranged offset in the circumferential direction.

[0083] Further with reference to the Figure 2It is evident that the drive shaft 420 projects into space 380 through the second bearing unit 300 or through the main bearing body 305. A counterweight 430 is located in space 380 and is arranged on the drive shaft 420.

[0084] Furthermore, the Figure 2 It can be deduced that the eccentric drive 150 is arranged in space 380, comprising an eccentric shaft section 152 and an eccentric bearing body 155 arranged on the eccentric shaft section 152. The eccentric shaft section 152 can be formed by the drive shaft 420.

[0085] The first spiral unit 100 according to Figure 2The device has a first side 101 and a second side 102 opposite the first side 101 along the longitudinal axis X. On the first side 101, the first spiral unit 100 is mounted on the second bearing unit 300 by means of the axial bearing 190. The eccentric drive 150 is coupled to the first spiral unit 100 on the first side 101, and on the second side 102, a first spiral rib 110 is arranged, which projects along the longitudinal axis X and forms a first spiral channel 120.

[0086] Furthermore, a ring-pin coupling 350 is provided, which connects several ring-pin coupling pairs 351 (see Figures 4 or 5The ring-pin coupling pairs form the ring-pin coupling 350, which prevents a complete rotation of the first spiral unit 100 about the longitudinal axis X. The ring-pin coupling 350 couples the first spiral unit 100 to the second bearing unit 300 and comprises a pin 356 and an abutment, which can be formed by a recess 352 and a sleeve 354 arranged in the recess 352. The pin 356 can move within the abutment in a manner corresponding to its orbital path.

[0087] According to the illustrated embodiment, the abutment can be formed in the second bearing unit 300, and the pins 356 project from the first side 101 of the first spiral unit 100 and engage in the abutments of the second bearing unit 300. A ring-pin coupling pair 351 can have a connecting bore 360 ​​that penetrates the second bearing unit 300 or the main bearing housing 302.

[0088] Furthermore, the Figure 2It can be deduced that the first spiral rib 110 on the second side 102 of the first spiral unit 100 forms the spiral channel 120 with a spiral channel base. Furthermore, the spiral rib 110 has a first spiral rib tip at its end face, which may either have a seal or be designed as a flat tip. The first spiral channel 120 may also have an inner end region 125 and / or an outer end region 126.

[0089] The first spiral rib 110 is involute in shape and extends from the inner end region 125 to the outer end region 126. The inner end region 125 is located radially inside with respect to the longitudinal axis X, and the outer end region 126 is located radially outside with respect to the longitudinal axis X. The at least one spiral channel 120 is U-shaped and is bounded in the radial directions by the spiral rib 110 or a spiral wall of the spiral rib 110 and the spiral channel floor.

[0090] The second spiral unit 200 can be stationary and has a first side 201 and a second side 202 opposite the first side 201 in the longitudinal axis X. On the first side 201, a second spiral rib 210 projects in the longitudinal axis X, the second spiral rib 210 forming a second spiral channel 220.

[0091] Furthermore, the second spiral rib 210 has a second spiral rib tip at its end face, which may either have a seal or be designed as a flat tip. The second spiral channel 220 may also have an inner end region 225 and / or an outer end region 226.

[0092] The second spiral rib 210 is adapted to the first spiral rib 110 and is also involute-shaped, extending from the inner end region 225 to an outer end region 226. The inner end region 225 is located radially inside with respect to the longitudinal axis X, and the outer end region 226 is located radially outside with respect to the longitudinal axis X. The at least one second spiral channel 220 is U-shaped and is bounded in the radial directions by the second spiral rib 210 or a spiral wall of the second spiral rib 210 and the bottom of the second spiral channel.

[0093] As in Figure 2As shown, the first spiral rib 110 of the first spiral unit 100 and the second spiral rib 210 of the second spiral unit 200 interlock. The first spiral unit 100 can be moved by the drive unit 400 along an orbital path (not shown) relative to the second spiral unit 200. A ring-pin coupling 350 prevents the first spiral unit 100 from rotating about its longitudinal axis X while moving along the orbital path.

[0094] During interlocking or interpenetration, the first spiral rib 110 engages in the second spiral channel 220 and the second spiral rib 210 engages in the first spiral channel 120. The second spiral rib tip of the second spiral rib 210 seals against the spiral channel base of the first spiral unit 100, and the first spiral rib tip of the first spiral rib 110 seals against the spiral channel base of the second spiral unit 200.

[0095] In a compressor, as the first spiral unit 100 moves along its orbital path, pressure chambers (not shown) are enclosed between the first spiral unit 100 and the second spiral unit 200. The medium is transferred through these chambers from the outer end regions 126, 226 to the inner end regions 125, 225. The outer end regions 126, 226 together form the intake region 320, from which the medium can be drawn into the spiral channels 120, 220. It is then transferred in closed pressure chambers (not shown) from the outer end region 126, 226 to the inner end region 125, 225, with the pressure chambers undergoing a continuous reduction in volume.

[0096] In an expander, as the first spiral unit 100 moves along its orbital path, pressure chambers (not shown) are enclosed between the first spiral unit 100 and the second spiral unit 200. These chambers displace the medium from the inner end regions 125 to 225 and the outer end regions 126, 226. During this process, the pressure chambers undergo a continuous increase in volume.

[0097] The medium is guided within the machine housing 10 along several flow paths from the inlet 11 to the outer end regions 126, 226, whereby the medium is used along these flow paths to cool the components in the machine housing 10 and / or to lubricate them with entrained lubricant. In the Figures 2-5 The flow paths are indicated by arrow lines, with only some of the arrow lines marked with the reference symbol "S" for better understanding.

[0098] The medium enters the machine housing 10 through inlet 11 and into the inlet section. From the inlet section, the medium then flows into the drive section.

[0099] In the inlet section, the medium branches out and flows along two parallel flow paths towards the drive section, one of the flow paths being guided through the first bearing unit 550 and the other flow path being guided through the drive shaft 420 or through the hollow shaft section 424 of the drive shaft 420.

[0100] The medium can flow from the hollow shaft section 424 into the drive section through the radial bore 428 of the drive shaft 420. The drive shaft 420 can have one or more radial bores 428 both between the first bearing unit 450 and the rotor 410, and between the rotor 410 and the second bearing unit 300, causing the flow path through the hollow shaft section 424 to branch multiple times and be used for cooling and / or lubrication of, for example, the rotor 410, the first bearing unit 300, and / or the second bearing unit 450.

[0101] Furthermore Figure 2It can be deduced that the drive unit 400 has at least one axial opening 414 and / or at least one axial groove 418, each of which guides a flow path through the drive unit 400. The respective axial opening 414 and the respective axial groove 418 connect the two opposite end faces of the drive unit 400, thereby allowing the drive unit 400 to be "flushed" with the medium. This measure enables very effective cooling of the drive unit 400.

[0102] The at least one axial opening 414 can be formed by a running gap between the rotor 410 and the stator 415.

[0103] From the drive section, the medium then flows along several flow paths through the second bearing unit 300 into the intake area 320.

[0104] On the one hand, the medium can be guided to the intake area 320 via the space 380 and on the other hand via the connecting bore 360 ​​in the ring-pin coupling 350 or in the at least one ring-pin coupling pair 351.

[0105] The medium can be guided from the inlet 11 into the chamber 380 along two parallel flow paths, one of which leads through the inlet openings 370 and the other through the main bearing body 305. In this way, the main bearing body 305 can be both cooled and lubricated by the lubricant carried along with the medium.

[0106] In space 380, the medium flows around the balancing mass 430 and the eccentric drive 150 of the first spiral unit 100, thereby allowing these components to be both cooled and lubricated.

[0107] The medium can cover the space 380 - as shown in the enlarged illustration according to Figures 3 and 5The fluid can be extracted and exit through the outlet openings 390, which connect the chamber 380 with the intake area 320 and the outer end areas 126, 226 of the first spiral unit 100 and the second spiral unit 200, respectively. The outlet openings 390 open into the intake area 320 on the second side of the second bearing unit 300 facing the first spiral unit 100, with each outlet opening 390 preferably opening within an area that is wholly or partially traversed by the first spiral unit 100 during a complete movement along its orbital path. The positioning of the outlet openings 390 allows the first side of the first spiral unit 100 and the axial bearing 190 to be lubricated by the lubricant carried by the medium.

[0108] To avoid damage to the respective outlet opening 390 and / or the axial bearing surface of the first spiral unit 100, it is possible - as in Figure 3As shown, the first spiral unit 100 has a recess 290 on the side facing the at least one outlet opening 390, which is arranged within a surface that the at least one outlet opening 390 passes over during a complete movement along the orbital path. Thus, the respective outlet opening 390 and the first spiral unit 100 do not come into contact.

[0109] A flow path can be routed from the drive section and the intake area 320 through the ring-pin coupling 350 or the ring-pin coupling pairs 351. Each ring-pin coupling pair 351 can have a connecting bore 360 ​​(see Figure 5) that provides a further flow path from the inlet 11 to the intake area 320. For this purpose, the connecting bores 360 penetrate the second bearing unit 300 and connect the first side of the second bearing unit 300 to the recess 352 of the first spiral unit 100. The connecting bores 360 in the ring-pin coupling pairs 351 reduce the pressure drop of the medium.

[0110] According to a further development not shown, at least one connecting bore 360 ​​can be provided which breaks through the second bearing unit 300 between two ring-pin coupling pairs 351 and leads a flow path from the inlet 11 to the intake area 320.

[0111] According to a further development not shown, the outlet openings 390 can be formed by several radially oriented axial recesses arranged on the second side of the second bearing unit 300.

[0112] The axial recesses can extend over the second side of the second bearing unit 300 and thus also over the axial bearing 190 formed between the second bearing unit 300 and the first spiral unit 100. The lubricant carried in the medium can contribute to the lubrication of the axial bearing 190 via the recessed areas when the first spiral unit 100 is traversed.

[0113] Furthermore, this embodiment can include an axial bearing element that can be arranged in a plate-like form between the second bearing unit 300 and the first spiral unit 100. The axial bearing element is preferably an axial bearing plate.

[0114] In both previously described embodiments, the high-pressure chamber 30 and the intermediate floor 50 are arranged on the second side 202 of the second spiral unit 200, the intermediate floor 50 being arranged along the longitudinal axis X between the high-pressure chamber 30 and the second spiral unit 200. The intermediate floor 50 decouples the second spiral unit 200 from the pressure forces in the high-pressure chamber 30 and is supported against the machine housing 10.

[0115] The high-pressure chamber 30 is connected to the second spiral channel 220 via a passage 260, wherein the passage 260 includes an outlet opening located in the region of the inner end regions 125, 225. The outlet opening, also called a "discharge port," is preferably formed in the inner end region 225 of the second spiral channel base, and the passage 260 extends along the longitudinal axis X through an opening in the intermediate base 50 to the high-pressure chamber 30.

[0116] The high-pressure chamber 30 is in turn connected to the outlet 12 and the medium can leave the scroll machine 2 through the outlet 12.

[0117] The high-pressure chamber 30 is enclosed by the machine housing 10 and the intermediate floor 50 and has the outlet 12 through which the medium can leave the scroll machine. For this purpose, the machine housing 10 or the second housing section 10'' can be cup-shaped with a recess, with the intermediate floor 50 acting as a lid or plug to close the high-pressure chamber 30 within the machine housing 10 or the second housing section 10''. For this purpose, the shapes of the recess in the second housing section 10'' and the intermediate floor 50 are adapted to each other, preferably with both the recess and the intermediate floor 50 having a circular cylindrical shape and being precisely fitted to each other.

[0118] To prevent leakage between the intermediate floor 50 and the machine housing 10, sealants may be provided there.

[0119] The intermediate floor 50 has a first side and a second side, the first side facing the second spiral unit 200, and the second side facing the high-pressure chamber 30.

[0120] The intermediate floor 50 includes the opening through which the passage 260 is routed.

[0121] In the illustrated embodiment, the intermediate floor 50 has an annular projection which extends on the first side of the intermediate floor 50 in the longitudinal axis X from the first side of the intermediate floor 50 in the direction of the second spiral unit 200.

[0122] On the first side of the intermediate floor 50, an axial locking device in the form of a retaining ring fixed in the machine housing 10 can be arranged, which determines the position of the intermediate floor 50 in the longitudinal axis X. The axial locking device supports the intermediate floor 50 on the side facing the second spiral unit 200 against the machine housing 10, thereby essentially decoupling the pressure forces from the high-pressure chamber 30 from the second spiral unit 200 and coupling them into the machine housing 10.

[0123] The second spiral unit 200 can telescopically encompass the annular projection of the intermediate floor 50 and for this purpose has a first annular projection and a second annular projection on the second side 202, wherein the first annular projection interacts with an inner surface of the annular projection and the second annular projection with an outer surface of the annular projection of the intermediate floor 50.

[0124] The annular projection of the intermediate floor 50, as well as the annular projections surrounding the annular projection of the intermediate floor 50 on the second side 202 of the second spiral unit 200, are not mandatory but represent a preferred embodiment that can be used particularly when the scroll machine 1 has an injection system or an Eco-Port. The annular projections of the intermediate floor 50 and the annular projections of the second spiral unit 200 can form a radial bearing for the second spiral unit 200.

[0125] The medium can be used - as shown by the arrow lines in Figure 2 As shown, the medium flows from the high-pressure chamber 30 via a pressure port 40 to the outlet 12, the pressure port 40 preferably being arranged in such a way that the medium cannot flow directly from the passage 260 into the pressure port 40.

[0126] The pressure nozzle 40 projects from the side of the machine housing 10 facing the intermediate floor 50 in the direction of the intermediate floor 50 and is arranged in a plane perpendicular to the longitudinal axis X offset from the passage 260 according to the figure 7.

[0127] To achieve a particularly effective reduction of pressure fluctuations in the high-pressure chamber 30, a backflow area 45 can be provided, which forces an S-shaped flow path S from the passage 260 through the pressure port 40 to the outlet 12, which in Figure 2 is indicated by an arrow line.

[0128] The backflow area 45 can have a preferably annular recess 59 on the second side of the intermediate floor 50, which faces the high-pressure chamber 30 (see Figure 6 ) exhibiting, which together with the pressure nozzle defines the S-shaped flow path. The pressure nozzle 40 is connected to the intermediate plate 50 according to the Figure 6in a contact area 46 in operative contact, wherein the contact area 46 is arranged on an imaginary connecting line in a plane perpendicular to the longitudinal axis X between the pressure port 40 and the passage 260. As a result, the medium coming from the passage 260 must first undergo a deflection in order to flow into the recess 59 and from there through the pressure port 40 to the outlet 12.

[0129] Between the high-pressure chamber 30 and the outlet 12, a Figure 2 The shown check valve 48 is arranged, which preferably includes a bushing 49 that can be inserted into the pressure port 40. Reference symbol list

[0130] 1 Refrigeration unit 2 Scrolling machine 3 Condenser 4 Expansion valve 5 Evaporator 10 Machine housing 11 Inlet 12 Outlet 30 High-pressure chamber 40 Pressure port 45 Backflow area 46 Contact area 49 Bushing 50 Intermediate plate 100 First spiral unit 101 First side 102 Second side 110 First spiral rib 120 First spiral channel 125 Inner end section 126 Outer end section 150 Eccentric drive 152 Eccentric shaft section 155 Eccentric bearing body 190 Thrust bearing 200 Second spiral unit 201 First side 202 Second side 210 Second spiral rib 225 Inner end section 226 Outer end section 220 Second spiral channel 260 Passage 290 Recess 320 Intake area 300 Second bearing unit 302 Main bearing housing 305 Main bearing body 350 Ring-pin coupling 351 Ring-pin coupling pair 352 Recess 354 Sleeve 356 Bolt 360 Connecting bore 370 Inlet opening 380 Space 390 Outlet opening 392 First bore section 394 Second bore section 400 Drive unit 410 Rotor 414 Axial groove 415 Stator 418 Axial opening 420 Drive shaft 424 Hollow shaft section 428 Radial bore 430 Balancing mass 450 First bearing unit 452 Bearing mount 455 Sub-bearing body

Claims

1. Scroll machine (2), in particular a scroll compressor, for a medium, in particular a refrigerant, comprising a machine housing (10) with a longitudinal axis (X) and an inlet and an outlet for the medium, wherein in the machine housing (10) along the longitudinal axis (X) a drive unit (400) with a drive shaft (420), which is mounted on the machine housing (10) by a first bearing unit (450) and a second bearing unit (300), a first scroll unit (100) with a scroll passage (120) formed by a first scroll wrap (110) with an inner end region (125) and an outer end region (126), a second scroll unit (200) with a scroll passage (220) formed by a second scroll wrap (210) with an inner end region (225) and an outer end region (226) are provided, and wherein the first scroll unit (100) and the second scroll unit (200) intermesh to form pressure chambers, wherein the first scroll unit (100) can be moved by the drive shaft (420) by the drive unit (400) along an orbital path relative to the second scroll unit (200), wherein the inlet (11) is in fluid communication with the outer end regions (126, 226) and the outlet (12) is in fluid communication with the inner end regions (125, 225), characterized in that the medium can flow in the machine housing (10) along a plurality of flow paths from the inlet (11) to the outer end regions (126, 226), wherein the second bearing unit (300) and the first scroll unit (100) enclose a space (380), and that at least one of the flow paths passes through the space (380), wherein the drive shaft (420) projects through the second bearing unit (300) into the space (380) and on the drive shaft (420) in the space (380) a balancing mass fixedly connected to the drive shaft (420) and / or an eccentric drive (150) for the first scroll unit (100) are / is arranged, wherein the space (380) has at least one exit opening (390), and that the exit opening (390) specifies a flow path that connects the space (380) with the outer end regions (126, 226).

2. Scroll machine (2) according to claim 1, characterized in that the drive shaft (420) has a hollow-shaft section (424) through which one of the flow paths is guided.

3. Scroll machine (2) according to claim 2, characterized in that the hollow-shaft section (424) is formed by a blind bore, and that the drive shaft (420) has at least one radial bore (428) breaking through the drive shaft (420) from the hollow-shaft section (424).

4. Scroll machine (2) according to one of claims 2 or 3, characterized in that a rotor (410) of the drive unit (400) is arranged between the first bearing unit (450) and the second bearing unit (300), and that the drive shaft (420) has the at least one radial bore (428) between the first bearing unit (450) and the rotor (410) and / or between the second bearing unit (300) and the rotor (410).

5. Scroll machine (2) according to claim 4, characterized in that the drive unit (400) has at least one axial opening (414) and / or at least one axial groove (418), and that the at least one axial opening (414) and / or the at least one axial groove (418) specifies one of the flow paths.

6. Scroll machine (2) according to one of claims 2 to 5, characterized in that between the inlet (11) and the drive shaft (420) a flow path branches into two flow paths connected in parallel, wherein one of the flow paths is guided through the hollow-shaft section (424) and the other of the flow paths is conducted through the first bearing unit (450).

7. Scroll machine (2) according to one of the preceding claims, characterized in that the second bearing unit (300) comprises a main bearing housing (302) and a main bearing body (305), and that at least one of the flow paths is guided through the main bearing housing (302) and / or the main bearing body (305).

8. Scroll machine (2) according to one of claims 6 or 7, characterized in that at least two flow paths coming from the inlet (11) lead through the second bearing unit (300) into the space (380), wherein one of the flow paths is guided through the main bearing body (305) and the other of the flow paths is guided through at least one entry opening (370) formed as an opening in the main bearing housing (302).

9. Scroll machine (2) according to claim 8, characterized in that a plurality of entry openings (370) are arranged over the circumference, preferably symmetrically.

10. Scroll machine (2) according to one of the preceding claims, characterized in that the at least one exit opening (390) is formed on the side facing the first scroll unit (100) as a radially oriented axial recess.

11. Scroll machine (2) according to one of the preceding claims, characterized in that the at least one exit opening (390) has a radially oriented first bore section (392) and an axially oriented second bore section (394).

12. Scroll machine (2) according to one of the preceding claims, characterized in that the at least one exit opening (390) is arranged offset in the circumferential direction relative to the at least one entry opening (370).

13. Scroll machine (2) according to one of the preceding claims, characterized in that the at least one exit opening (390) on the side facing the first scroll unit (100) opens partially or completely within an area that is traversed during a complete movement of the first scroll unit (100) along the orbital path.

14. Scroll machine (2) according to one of the preceding claims, characterized in that the first scroll unit (100) on the side facing the at least one exit opening (390) has a step-back (290) which is arranged within an area over which the at least one exit opening (390) passes during a complete movement along the orbital path.

15. Scroll machine (2) according to one of the preceding claims, characterized in that a ring-pin coupling (350) is provided, and that one of the flow paths is guided through the ring-pin coupling (350).

16. Scroll machine (2) according to one of the preceding claims, characterized in that the second scroll unit (200) is stationary.

17. Scroll machine (2) according to one of the preceding claims, characterized in that in the machine housing a high-pressure chamber (30) is arranged, that the inner end regions (125, 225) are connected via a passage (260) with the high-pressure chamber (30) and via the high-pressure chamber (30) with the outlet (12), and that in the high-pressure chamber (30) a backflow region (45) is provided which forces an S-shaped flow path in the high-pressure chamber (30).

18. Scroll machine (2) according to claim 17, characterized in that between the high-pressure chamber (30) and the second scroll unit (200) an intermediate floor (50) is provided and that the backflow region (45) is formed by a recess (59) formed in the intermediate floor (50) on the side facing the high-pressure chamber (30) and by a pressure connection piece (40) projecting toward the recess (59).

19. Scroll machine (2) according to claim 17 or 18, characterized in that the pressure connection piece (40) is in operative contact with the intermediate floor (50) in a contact region (46) to form the backflow region (45), and that the contact region (46) is arranged on an imaginary connecting line in a plane perpendicular to the longitudinal axis (X) between the pressure connection piece (40) and the passage (260).

20. Scroll machine (2) according to one of claims 17 to 19, characterized in that the pressure connection piece (40) comprises a bushing (49) with a non-return valve.

21. Refrigeration system (1) with a scroll machine (2) according to one of the preceding patent claims.