DISPLACEMENT MACHINE, METHOD, VEHICLE AIR CONDITIONING AND VEHICLE

Description

[0001] The invention relates to a displacement machine based on the spiral principle according to the preamble of claim 1. Furthermore, the invention relates to a method, a vehicle air conditioning system, and a vehicle.

[0002] A positive displacement machine of the type mentioned above is known from DE 10 2017 110 913 B3 and US 2015 / 104342 A1. These documents describe a scroll compressor comprising a displacer spiral and a counter-spiral. The displacer spiral engages with the counter-spiral. The orbiting displacer spiral forms compression chambers in which a coolant is compressed. For the coolant to be compressed, the displacer spiral must be in close contact with the counter-spiral. Therefore, it is advantageous for the displacer spiral to be pressed against the counter-spiral. For this purpose, a back-pressure chamber is arranged on the side of the displacer spiral facing away from the counter-spiral. Such a back-pressure chamber is also known as a back-pressure chamber. The back-pressure chamber serves to build up pressure. For this purpose, the displacement spiral includes an opening which leads to the counter-pressure chamber orThe back-pressure chamber is fluidly connected to a compression chamber. The pressure in the back-pressure chamber exerts a force on the displacer spiral, pressing it against the counter-spiral, so that the two spirals are fluid-tightly sealed against each other.

[0003] In known scroll compressors of the type mentioned above, the pressure in the back pressure chamber must be just high enough to press the displacer spiral against the counter spiral in such a way that the displacer spiral is in a fluid-tight seal against the counter spiral. However, the pressure should not be too high, otherwise frictional forces will occur that slow down the orbiting movement of the displacer spiral or lead to a loss of performance.

[0004] Providing a sufficiently high pressure for the counter-pressure chamber to press the displacement spiral against the counter-spiral while causing as little power loss as possible involves considerable design effort.

[0005] The present invention is therefore based on the objective of providing a displacement machine in which the generation of the pressure for pressing the displacement spiral against the counter spiral is improved, such that a simple and cost-effective construction of the displacement machine is possible. Furthermore, it is an object of the invention to provide a method, a vehicle air conditioning system, and a vehicle.

[0006] According to the invention, the problem is solved with regard to the displacement machine is solved by the subject matter of claim 1, the method by the subject matter of claim 13, the vehicle air conditioning system by the subject matter of claim 14 and the vehicle by the subject matter of claim 15.

[0007] Specifically, the problem is solved by a positive displacement machine based on the spiral principle, in particular a scroll compressor, comprising a high-pressure chamber, a low-pressure chamber, an orbiting positive displacement spiral, a counter-spiral, and a back-pressure chamber arranged between the low-pressure chamber and the positive displacement spiral. The positive displacement spiral engages with the counter-spiral such that, during operation, at least a first and a second compression chamber are temporarily formed for receiving a working fluid, and the positive displacement spiral has at least one through-opening for fluid communication with the back-pressure chamber. The through-opening is arranged in the positive displacement spiral such that, during operation, the orbiting movement of the positive displacement spiral causes the through-opening to be temporarily located at least partially in the first compression chamber and subsequently at least partially in the second compression chamber.

[0008] The high-pressure chamber is the area into which the compressed working medium flows before it is fed back into a circuit, e.g. a cooling circuit.

[0009] The low-pressure chamber can also be called the intake chamber. Gas flows radially outwards from the low-pressure chamber between the counter-spiral and the displacement spiral.

[0010] The orbiting motion of the displacement spiral is understood to mean a movement along a circular path.

[0011] The working medium is preferably a cooling fluid, particularly preferably a gaseous cooling fluid, for example CO2.

[0012] At least one first compression chamber and one second compression chamber are arranged between the counter-spiral and the displacement spiral. During operation, a working medium or fluid is contained in the compression chambers.

[0013] The compression chambers form in the radially outer area. These chambers migrate radially inwards. As they migrate, their volume decreases. This increases the pressure within the chambers, thus compressing the working fluid. Finally, the compression chambers merge and then dissolve. This process occurs continuously.

[0014] The through-hole moves along a circular path due to the orbiting motion of the displacement spiral. The circular path of the through-hole overlaps with the first compression chamber and the second compression chamber in such a way that the through-hole is temporarily located, at least partially, in the first and then in the second compression chamber, thus forming a fluid connection with the counter-pressure chamber.

[0015] In other words, the through-opening covers the first compression chamber and the second compression chamber in such a way that the through-opening is temporarily located at least partially in the first and then in the second compression chamber, and a fluid connection with the counter-pressure chamber is formed.

[0016] The through-opening changes from the first compression chamber to the second compression chamber due to the orbiting movement of the displacement spiral. This results in the counter-pressure chamber being alternately and temporarily fluidly connected to the first and second compression chambers. According to the invention, the first compression chamber is fluidly connected to the counter-pressure chamber within an angular range of the rotation angle of the orbiting displacement spiral from 120° to 400°, in particular from 247° to 367°.

[0017] It is possible that more than two compression chambers are formed between the displacement spiral and the counter-spiral, and that the through-opening is temporarily arranged in more than two compression chambers, at least section by section.

[0018] The invention is advantageous because the temporary, sequential arrangement of the through-opening in at least two different compression chambers makes it possible to generate pressure in the counter-pressure chamber to press the displacer spiral against the counter-spiral in such a way that the frictional forces, which slow down the orbiting movement of the displacer spiral or otherwise negatively affect it, are minimized, and at the same time the displacer spiral is arranged with sufficient fluid tightness against the counter-spiral. The force exerted by the displacer spiral on the counter-spiral is caused by the pressure prevailing in the counter-pressure chamber.

[0019] Additional fluid connections that pressurize and / or influence the pressure within the counter-pressure chamber are thus eliminated. In other words, the through-hole in the displacement spiral is sufficient to generate adequate pressure in the counter-pressure chamber. This allows for a more compact design, as additional fluid connections are no longer necessary. Furthermore, time and costs are saved due to the reduced manufacturing effort.

[0020] Preferred embodiments of the invention are specified in the dependent claims.

[0021] In a particularly preferred embodiment, the counter-spiral comprises spiral sections, wherein the through-opening passes through at least one spiral section when changing from the first compression chamber to the second compression chamber, which is arranged between two compression chambers adjacent to each other in a radial direction.

[0022] The spiral sections are understood to be the sections of the counter-spiral or the displacement spiral that define the first compression chamber and the second compression chamber.

[0023] Passing through the spiral sections is advantageous because in this way the transition between the compression chambers can be defined and the arrangement of the through-opening in the two compression chambers can take place immediately one after the other.

[0024] The term "passing" means crossing a spiral segment in a radial direction or in a direction with a radial component. The spiral segment can be crossed completely and / or in sections.

[0025] In another particularly preferred embodiment, the through-opening is arranged in a section of the bottom of the displacement spiral.

[0026] It is advantageous to position the through-opening in the base of the displacement spiral, as this facilitates the passage of the spiral sections through the opening. Furthermore, this allows for a straight and as short a connection as possible to the counter-pressure chamber.

[0027] The base plate is to be understood as the floor, from which the spiral sections extend orthogonally.

[0028] It is advantageous for the through-hole to have a circular, elliptical, or egg-shaped cross-section. This allows for various advantageous designs of the through-hole, which influence the flow characteristics of the working fluid. For example, the area of ​​the through-hole that is exposed first during operation when passing through a spiral section can have a larger cross-section than the area still covered by the spiral section. This makes it possible to establish good fluid communication with the backpressure chamber even before the through-hole is fully open.

[0029] In a preferred embodiment, the second compression chamber is fluidly connected to the counter-pressure chamber in an angular range of the rotation angle of the orbiting displacement spiral from 270° to 550°, in particular from 376° to 504°.

[0030] The angular ranges of the rotation angle in which the first and second compression chambers are fluidly connected to the counter-pressure chamber are advantageous, since a fluid connection of the compression chambers with the counter-pressure chamber is possible over as large a range as possible of the rotation angle of the orbiting displacement spiral.

[0031] The angular ranges for the first and second compression chambers are chosen such that the compression chambers are only fluidly connected to the counter-pressure chamber when the pressure in the first and second compression chambers is large enough to generate sufficient pressure in the counter-pressure chamber and to press the displacer spiral against the counter-spiral in a fluid-tight manner and with minimal loss of performance.

[0032] Particularly preferred is the first compression chamber fluidly connected to the counter-pressure chamber at a relative volume of 84% to 40%, especially from 80% to 46%.

[0033] Furthermore, the second compression chamber is particularly preferably fluidly connected to the counter-pressure chamber at a relative volume of 61% to 19%, especially from 44% to 24%.

[0034] The relative volume of the compression chambers refers to the changing volume of the compression chambers at a specific point in time during a compression cycle of the positive displacement machine, relative to the initial volume at a rotation angle of 0°. The smaller the relative volume of a compression chamber, the greater the pressure in that chamber.

[0035] The compression cycle refers to the periodic process characterized by the constantly forming compression chambers.

[0036] The ranges of relative volumes in which the first and second compression chambers are fluidly connected to the counter-pressure chamber are advantageous because this makes it possible for the compression chambers to be fluidly connected to the counter-pressure chamber only when the pressure in the respective compression chamber is sufficiently high to allow a fluid-tight pressing of the displacer spiral against the counter-spiral.

[0037] In one embodiment, the through-opening is closed for an angular range of 5° to 20° when passing through the spiral section during the change from the first to the second compression chamber or vice versa.

[0038] This makes it possible to keep the time the through-hole is closed as short as possible. More precisely, the time the through-hole is closed is so short that the effect on the pressure in the back-pressure chamber is minimal. Therefore, the time the through-hole is closed has no effect on the pressure in the back-pressure chamber or the contact force on the displacement spiral, and consequently, no effect on the function of the displacement machine.

[0039] In another embodiment, the through-opening has a control geometry that is arranged in the surface of the displacer spiral facing the counter-spiral.

[0040] The control geometry, for example, uses a spiral section to define a fluid channel that connects the through-hole to a compression chamber before the through-hole is located within the compression chamber. This control geometry allows the through-hole to be connected to the compression chamber earlier or for a longer period. As a result, the time the through-hole is closed by the spiral section can be reduced.

[0041] It is advantageous if the control geometry has a recess and / or a notch. This makes the control geometry easy to manufacture with known manufacturing tools and with minimal effort.

[0042] In a preferred embodiment, the spiral sections of the counter-spiral have a radially inner spiral wall and a radially outer spiral wall, wherein the control geometry and / or the through-hole is arranged between the spiral walls in the closed state.

[0043] The control geometry is advantageously designed such that the first and second through-holes are never fluidically connected to each other during the compression cycle. This prevents a pressure drop in the compression chambers.

[0044] In an advantageous embodiment, the displacer spiral and / or the counter spiral has a chamfer at least in sections. The chamfer reduces the width of the spiral section in that section. This reduces the range of rotation angle through which the through-hole moves to pass through the spiral section. The chamfer thus makes it possible to shorten the time the through-hole is closed.

[0045] Within the scope of the invention, a method for operating a displacement machine is further disclosed and claimed, in which the through-opening is temporarily arranged at least sectionally in the first compression chamber and subsequently at least sectionally in the second compression chamber by the orbiting movement of the displacement spiral during operation, and the respective compression chamber is fluidly connected to the counter-pressure chamber.

[0046] Within the scope of the invention, a vehicle air conditioning system with a displacement engine is disclosed and claimed.

[0047] As a further aspect of the invention, a vehicle with a displacement engine according to the invention or a vehicle air conditioning system is disclosed and claimed.

[0048] The invention will be explained in more detail below using exemplary embodiments with reference to the accompanying drawings.

[0049] It shows: Fig. 1 shows a schematic section of a counter-spiral and a displacer spiral of an embodiment of a displacement machine according to the invention; Fig. 2 shows a schematic section of a counter-spiral and a displacer spiral of an embodiment of a displacement machine according to the invention during a compression cycle at a rotation angle of 0°; Fig. 3 shows a schematic section of the displacement machine according to Fig. 2 at a rotation angle of 60°; Fig. 4 a schematic section of the displacement machine according to Fig. 2 at a rotation angle of 160°; Fig. 5 a schematic section of the displacement machine according to Fig. 2 at a rotation angle of 300°; Fig. 6 a schematic section of the displacement machine according to Fig. 2 at a rotation angle of 400°; Fig. 7 a schematic section of the displacement machine according to Fig. 2 at a rotation angle of 460°; Fig. 8 a schematic section of the displacement machine according to Fig. 2 at a rotation angle of 560°; Fig. 9 a section through a displacement spiral of an embodiment of a displacement machine according to the invention; Fig. 10 a section through an embodiment of a displacement machine according to the invention; Fig. 11 a further section through the displacement machine according to Fig. 10 .

[0050] Fig. 1 shows a schematic view of the arrangement of a displacer spiral 13 and a counter-spiral 14 in a displacer machine 10.

[0051] The displacer spiral 13 and the counter-spiral 14 are in engagement with each other. Both the displacer spiral 13 and the counter-spiral 14 have spiral sections 18 arranged orthogonally on a base plate. The base plate is circular. The spiral sections 18 extend away from the base plate. In the installed state, the spiral sections of the displacer spiral 13 extend towards the counter-spiral 14, and the spiral sections 18 of the counter-spiral 14 extend towards the displacer spiral 13.

[0052] The counter-spiral 14 is fixed or immovable within the displacement machine 10. The displacement spiral 13 is arranged within the displacement machine 10 such that orbiting motion is possible within the counter-spiral 14. The construction of the displacement machine 10 will be described in the following section. Fig.10 and Fig. 11 This will be explained in more detail. Orbital motion refers to movement along a circular path.

[0053] An outlet opening 22 is arranged in the area of ​​the center or midpoint of the counter-spiral. The outlet opening 22 is arranged off-center in the counter-spiral 14.

[0054] The positions of the displacement spiral 13 during a compression cycle can be represented by the rotation angle of the orbiting motion. A compression cycle is understood to be one iteration or one period of the continuously recurring compression process. Thus, it shows Fig. 1 a point in time in a compression cycle of the displacement machine 10 at a rotation angle of the displacement spiral 13 of 181°.

[0055] A through-opening 17 is arranged in the displacement spiral 13. The through-opening 17 is located in the base or base plate of the displacement spiral 13. It is positioned centrally between two spiral sections 18 of the displacement spiral 13. The through-opening 17 runs perpendicular to the surface of the base. In the installed state, the through-opening 17 extends between one side of the base plate facing the counter-spiral 14 and the other side of the base plate facing away from the counter-spiral 14. The through-opening 17 has an opening on each side of the base plate, connecting the two sides of the base or base plate. In other words, the through-opening 17 forms a passage between the two sides of the base plate. The through-opening 17 has a circular cross-section. Other shapes are possible. The through-opening 17 preferably has a bore.The diameter of the through-hole 17 is preferably between 0.1 mm and 1 mm.

[0056] The through-opening 17 has a control geometry 19 for controlling the flow characteristics of the working medium.

[0057] The control geometry 19 extends essentially in a radial direction along the displacement spiral 13. In other words, the direction in which the control geometry 19 extends has a radial component. Alternatively, other shapes and directions of the control geometry 19 are possible. The control geometry 19 extends radially outward from the through-opening 17 along the displacement spiral 13.

[0058] The control geometry 19 is arranged in a surface of the base or base plate of the displacement spiral 13. The control geometry 19 does not penetrate the base of the displacement spiral 13.

[0059] The control geometry 19 has a slot. The slot is straight. The through-opening 17 is arranged at a radially inner end. The radially outer end of the control geometry has a circular section. Other shapes are possible. The control geometry 19 is preferably designed as a milled groove or notch.

[0060] The spiral sections 18 of the counter-spiral 14 have a radially inner spiral wall 20a and a radially outer spiral wall 20b. The dimension of the control geometry 19 and the through-opening 17 extends between the radially inner spiral wall 20a and the radially outer spiral wall 20b. The control geometry 19 and the through-opening 17 do not project beyond the spiral walls 20a, 20b. In other words, if the control geometry 19 and a spiral section 18 are superimposed, the control geometry 19 and the through-opening 17 do not project beyond the side walls 20a, 20b, but are completely concealed.

[0061] Between the displacement spiral 13 and the counter-spiral 14, a first compression chamber 16a and a second compression chamber 16b are formed. The compression chambers 16a and 16b serve to hold and compress a working medium. A gaseous coolant, for example, is a possible working medium. The compression chambers 16a and 16b are described in more detail below.

[0062] The displacement spiral 13 and the counter-spiral 14 each have a chamfer 21 along the spiral walls 20a, 20b. The chamfer 21 extends along the entire spiral turn. Alternatively, the chamfer 21 is arranged section by section on the spiral segments 18. Thus, it is possible that the chamfer 21 is only arranged in those areas of the spiral segments 18 where the through-opening 17 passes through the spiral segments 18 during the transition between the two compression chambers 16a, 16b.

[0063] In Fig. 2 bis Fig. 8 Various states of a compression cycle of a displacement machine 10 are schematically represented. The relative positions of the displacement spiral 13 and the counter-spiral 14 to each other are described below as snapshots with regard to the geometry of the respective components.

[0064] Fig. 2 shows a schematic view of a compression cycle with a displacer spiral 13 and a counter-spiral 14 engaged with each other, at a rotation angle of 0°.

[0065] The compression cycle of the positive displacement machine 10 begins at a rotation angle of 0°. A rotation angle of 0° describes the state in which one of the at least two compression chambers 16a, 16b is closed. It is possible that both compression chambers are closed at 0°.

[0066] A compression chamber is closed when the compression chamber is fluid-tightly enclosed by the displacer spiral 13 and the counter spiral 14.

[0067] The first compression chamber 16a is still open. The second compression chamber 16b is closed. Compression chambers 16a and 16b are located in the radially outer region of the spirals 13 and 14. In the radially inner region of the displacer spiral 13 and the counter-spiral 14, two further first and second compression chambers 16c and 16d from a previous compression cycle are formed. The relative volume of compression chambers 16a and 16b is larger than the relative volume of compression chambers 16c and 16d.

[0068] In the area of ​​the center of the arrangement of the displacement spiral 13 and the counter-spiral 14, an inner compression chamber 23 is arranged. The inner compression chamber 23 is formed from two compression chambers joined together.

[0069] Additionally, two secondary outlet openings 22a and 22b, or pre-outlet openings, are arranged between the outlet opening 22 and the radially outer region of the counter-spiral 14. The secondary outlet openings 22a and 22b each have different radial distances from the center of the counter-spiral 14.

[0070] The through-opening 17 with the control geometry 19 is arranged in the displacement spiral 13. The through-opening 17 and the control geometry 19 are covered by a spiral section 18 of the counter-spiral 14. The through-opening 17 is therefore closed.

[0071] Fig. 3 shows a snapshot of the compression cycle at a rotation angle of the displacer spiral 13 of 60°. In Fig. 3 Both compression chambers 16a and 16b are closed. The relative volumes of the compression chambers 16a and 16b in Fig. 3 are smaller than the relative volumes of the compression chambers 16a, 16b in Fig. 2 .

[0072] The through-opening 17 and the control geometry 19 are arranged in the compression chamber 16d. In other words, the through-opening 17 is not covered or closed by a spiral section 18.

[0073] Fig. 4 Figure 1 shows a view of the compression cycle at a rotation angle of 160°. The relative volumes of the compression chambers 16a and 16b are smaller than in the previously described figures.

[0074] The through-opening 17 is covered by a spiral section 18 of the counter-spiral 14. The control geometry 19 partially projects into the first compression chamber 16a. The through-opening 17 is therefore fluidly connected to the first compression chamber 16a.

[0075] Compression chambers 16c and 16d have merged to form the inner compression chamber 23.

[0076] Fig. 5 Figure 1 shows a view of the compression cycle at a rotation angle of 300°. The relative volumes of the first and second compression chambers 16a, 16b have decreased further. New compression chambers 16e, 16f begin to form in the radially outer region of the two spirals.

[0077] The through-opening 17 and the control geometry 19 are completely arranged in the first compression chamber 16a.

[0078] Fig. 6 Figure 1 shows the compression cycle at a rotation angle of 400°. In the radially outer region of the displacer spirals 13, 14, two new compression chambers 16e, 16f have formed. The relative volumes of the compression chambers 16a, 16b have decreased further. The through-opening 17 and a section of the control geometry 19 are located in the second compression chamber 16b. Part of the control geometry 19 is obscured by the spiral section 18 of the counter-spiral 14. The outlet opening 22 is partially located in the inner compression chamber 23 and in the second compression chamber 16b.

[0079] Fig. 7 Figure 1 shows the compression cycle at a rotation angle of 460°. The relative volumes of the first and second compression chambers 16a and 16b have decreased further. The through-hole 17 and the control geometry 19 are located entirely within the second compression chamber 16b. The outlet opening 22 is located within the second compression chamber 16b. The outlet opening 22 is partially covered by the displacer spiral 13.

[0080] Fig. 8 Figure 1 shows the compression cycle at a rotation angle of the displacer spiral 13 of 560°. The first and second compression chambers 16a, 16b have merged to form an inner compression chamber 23. The outlet opening 22 is located entirely within the inner compression chamber 23. The through-hole 17 and the control geometry 19 are located entirely within the newly formed first compression chamber 16e.

[0081] Fig. 9 Figure 1 shows a section through the displacer spiral 13 in the area of ​​the through-opening 17 and the control geometry 19. The through-opening 17 extends in a straight line. The through-opening 17 extends orthogonally to the surface of the displacer spiral 13. The surface here refers to the surface facing the counter-spiral 14.

[0082] The control geometry 19 is arranged in the surface of the displacer spiral 13. In other words, the control geometry 19 comprises a recess. Possible embodiments of the control geometry 19 include, for example, a notch or a milled groove. It is also possible for the control geometry 19 to comprise a gap, which is open towards the counter-spiral 14 and closed towards the displacer spiral 13. The control geometry 19 extends along a radial direction of the displacer spiral 13. Other orientations and geometries for the control geometry are conceivable. For example, it is also possible for the control geometry 19 to be non-straight.

[0083] The Fig. 10 and Fig. 11 Each shows sections through an embodiment of a displacement machine according to the invention 10.

[0084] The displacement machine 10 comprises a housing 24. The housing 24 has a cylindrical shape. A drive 25 is arranged in the housing 24. The drive 25 could be, for example, an electric motor or a mechanical drive 25. The drive 25 is connected to a shaft 26 and drives the shaft 26.

[0085] The shaft 26 extends longitudinally along the housing 24. An eccentric bearing 27 with an eccentric pin is arranged at one axial end of the shaft 26. The displacement spiral 13 is connected to the shaft 26 via the eccentric bearing 27.

[0086] On the side of the displacement spiral 13 facing away from the eccentric bearing 27, the counter spiral 14 is arranged in the housing 24. The counter spiral 14 is fixed and immovably arranged in the housing 24 of the displacement machine 10. It is possible that the counter spiral 14 is formed as a single piece with the housing 24.

[0087] A low-pressure chamber 12 is arranged on the side of the displacement spiral 13 facing away from the counter-spiral 14. A counter-pressure chamber 15 is arranged between the low-pressure chamber 12 and the displacement spiral 13.

[0088] The displacement spiral 13 is movably arranged in the housing 24 in a direction parallel to the longitudinal direction of the shaft 26. In other words, the displacement spiral 13 is displaceable towards and away from the counter-spiral 14. The through-opening 17 is located in the base of the displacement spiral 13. Through the through-opening 17, it is possible to connect the compression chambers 16 to the back-pressure chamber 15 via a fluid-conducting connection during operation.

[0089] A high-pressure chamber 11 is arranged on the side of the counter-spiral 14 facing away from the displacement spiral 13.

[0090] The interlocking spirals 13 and 14 form the compression chambers 16. In other words, the compression chambers 16 are bounded by the spiral sections 18 of the displacement spiral 13 and the counter-spiral 14.

[0091] The working medium, for example a coolant, is drawn in at the beginning of a compression cycle in a radially outer region of the spirals 13, 14. The working medium is transported in the compression chambers 16a, 16b between the displacer spiral 13 and the counter spiral 14.

[0092] During operation, the rotation of the shaft 26 and the eccentric connection of the displacement spiral 13 with the shaft 26 create the orbiting movement of the displacement spiral 13.

[0093] The orbiting motion of the displacement spiral 13 reduces the relative volumes of the compression chambers 16. The compression chambers 16 are temporary. They continuously reform in the outer radial region of the spiral arrangement and then migrate to the radial interior of the spiral arrangement, dissolving there. The movement path of the compression chambers 16 is spiral. In the embodiment shown in Fig. 2 bis 8 As shown, up to five compression chambers 16, 23 are possible. These consist of two pairs of first and second compression chambers 16 and one inner compression chamber 23. Configurations with more or fewer compression chambers 16, 23 are also possible.

[0094] The through-opening 17 forms a fluid connection between the first compression chamber 16a and the counter-pressure chamber 15 within an angular range of the rotation angle between 147° and 367°. Between the angular range of the rotation angle between 376° and 504°, the through-opening 17 forms a fluid connection with the second compression chamber 16b and the counter-pressure chamber 15. In the angular range of the rotation angle between 367° and 376°, the through-opening 17 is closed by a spiral section 18 of the counter-spiral 14.

[0095] The through-opening 17 is initially located in the first compression chamber 16a and subsequently in the second compression chamber 16b of a compression cycle. The through-opening 17 is located once in each of the compression chambers 16a and 16b per compression cycle. After the second compression chamber 16b, the through-opening 17 moves to the first compression chamber 16c of the following compression cycle.

[0096] Part of the working medium flows through the through-opening 17 into the counter-pressure chamber 15. This increases the pressure in the counter-pressure chamber 15. The pressure exerts a force on the displacement spiral 13 in the axial direction. This force acts in the direction of the counter-spiral 14. Since the displacement spiral 13 is movable in the axial direction, it is pressed against the counter-spiral 14. This pressure compresses the working medium with minimal loss of performance.

[0097] During operation, the control geometry 19 forms a fluid-conducting channel with the side of the counter-spiral 14 facing the displacement spiral. This makes it possible for a fluid-conducting connection to be formed between a compression chamber 16 and the counter-pressure chamber 15 before the through-opening 17 in a compression chamber 16 is fully or partially arranged.

[0098] The compressed working medium flows through the outlet opening 22 into the high-pressure chamber 11. From the high-pressure chamber 11, the working medium returns to a working circuit, in particular a cooling circuit. During operation, the secondary outlet openings 22a and 22b are positioned at different pressure zones of the positive displacement machine 10 due to their varying distances from the center point of the counter-spiral 14.

[0099] The following describes a compaction cycle based on... Fig. 2 bis Fig. 8 explained. In particular, the compression chambers 16a and 16b are considered.

[0100] Fig. 2 Figure 1 shows the compression cycle at a rotation angle of 0°. At a rotation angle of 0°, one of the at least two compression chambers 16a, 16b is closed. Fig. 2 No fluid connection is formed between one of the compression chambers 16 and the counter-pressure chamber 15, since the through-opening 17 with the control geometry 19 is completely covered by a spiral section 18.

[0101] With a rotation angle of 60° (see below). Fig. 3 The first and second compression chambers 16a and 16b are closed. The relative volumes of the compression chambers 16a and 16b decrease with increasing rotation angle. The through-hole 17 and the control geometry 19 move in a circular path.

[0102] With a rotation angle of 160° (see Fig. 4 The passage opening 17 has shifted further. The passage opening 17 is covered by the spiral section 18, which separates the first compression chamber 16a and the second compression chamber 16b. The passage opening 17 is not located in the first compression chamber 16a.

[0103] The control geometry 19 of the through-opening 17 is arranged section by section in the first compression chamber 16a. The control geometry 19 and the spiral section 18 define a channel. The back pressure chamber 15 is fluidly connected to the first compression chamber 16a through this channel.

[0104] At the in Fig. 5 With a rotation angle of 300° as shown, the through-opening 17 and the control geometry 19 are completely located within the first compression chamber 16a. The working medium can flow directly through the through-opening 17 into the counter-pressure chamber 15.

[0105] The pressure in the first compression chamber 16a is in Fig. 5 higher than in the first compression chamber 16a in Fig. 4 The pressure in the compression chambers 16a, 16b increases with the reduction of the relative volumes.

[0106] Fig. 6 Figure 1 shows that at a rotation angle of 400°, the through-opening 17 is located in the second compression chamber 16b. The through-opening 17 and the control geometry 19 have passed through the spiral section 18 of the counter-spiral 14. During passage through the spiral section 18, the through-opening 17 is closed by the spiral section 18.

[0107] The time period during which the counter-pressure chamber 15 is not connected to any compression chamber 16 is not sufficient for the pressure in the counter-pressure chamber to drop so that the displacer spiral 13 is no longer pressed fluid-tight against the counter-spiral 14.

[0108] In Fig. 7 The figure shows the state of the compression cycle at a rotation angle of 460°. The through-hole 17 and the control geometry 19 are completely located in the second compression chamber 16b. The first and second compression chambers 16a, 16b are about to merge and form the inner compression chamber 23. Fig. 7 It can be seen that a new compaction cycle begins at the same time as the current compaction cycle.

[0109] With a rotation angle of 560° (see Fig. 8 The first and second compression chambers 16a, 16b have merged to form the inner compression chamber 23. The through-opening 17 and the control geometry 19 are arranged in a subsequent first compression chamber 16e of the new compression cycle.

[0110] It is possible for several compression cycles to occur in parallel. The first and second compression chambers 16a, 16b and the first and second compression chambers 16c, 16d are assigned to different compression cycles. In other words, each compression cycle comprises a pair of first and second compression chambers 16a, 16b. Reference symbol list

[0111] 10 Displacement machine 11 High-pressure chamber 12 Low-pressure chamber 13 Displacement spiral 14 Counter-spiral 15 Counter-pressure chamber 16a First compression chamber 16b Second compression chamber 16c First compression chamber 16d Second compression chamber 16e First compression chamber 16f Second compression chamber 17 Through-opening 18 Spiral section 19 Control geometry 20a Radial inner spiral wall 20b Radial outer spiral wall 21 Chamfer 22 Outlet opening 22a Secondary outlet opening 22b Secondary outlet opening 23 Inner compression chamber 24 Housing 25 Drive 26 Shaft 27 Eccentric bearing

Claims

1. A displacement engine according to the spiral principle, in particular a scroll compressor, with a high-pressure chamber (11), a low-pressure chamber (12), an orbiting displacement spiral (13), a counter spiral (14), and a counter pressure chamber (15), which is arranged between the low-pressure chamber (12) and the displacement spiral (13), wherein the displacement spiral (13) engages into the counter spiral (14) so as to temporarily form at least a first and a second compression chamber (16a, 16b) during operation for receiving a working medium, and wherein the displacement spiral (13) has at least one through opening (17) for fluidly connecting with the counter pressure chamber (15), wherein the through opening (17) is arranged in the displacement spiral (13), such that the orbiting motion of the displacement spiral (13) during operation causes the through opening (17) to be at least sectionally temporarily arranged in the first compression chamber (16a), and subsequently at least sectionally temporarily arranged in the second compression chamber (16b), characterized in that the first compression chamber (16a) is connected in a fluid conducting manner with the counter pressure chamber (15) in an angular range of the rotation angle of the orbiting displacement spiral (13) of 120° to 400°, in particular of 247° to 367°, wherein the compression cycle of the displacement engine begins at the rotation angle of 0°.

2. The displacement engine according to claim 1, characterized in that the counter spiral (14) comprises spiral sections (18), wherein, during a switch from the first compression chamber (16a) to the second compression chamber (16b), the through opening (17) passes at least one spiral section (18) arranged between two compression chambers (16a, 16b) that abut each other in a radial direction.

3. The displacement engine according to claims 1 or 2, characterized in that the through opening (17) is arranged in a section of the floor of the displacement spiral (13).

4. The displacement engine according to any one of the preceding claims, characterized in that the through opening (17) has a circular, elliptical or oval cross section.

5. The displacement engine according to any one of the preceding claims, characterized in that the second compression chamber (16b) is connected with the counter pressure chamber (15) in a fluid conducting manner in an angular range of the rotation angle of the orbiting displacement spiral (13) of 270° to 550°, in particular of 376° to 504°.

6. The displacement engine according to any one of the preceding claims, characterized in that the first compression chamber (16a) is fluidically connected with the counter pressure chamber (15) at a relative volume of 84% to 40%, in particular of 80% to 46%.

7. The displacement engine according to any one of the preceding claims, characterized in that the second compression chamber (16b) is fluidically connected with the counter pressure chamber (15) at a relative volume of 61% to 19%, in particular of 44% to 24%.

8. The displacement engine according to any one of the preceding claims, characterized in that the through opening (17) is sealed for an angular range of the rotation angle of 5° to 20° while passing the spiral section (18) during a switch from the first to the second compression chamber (16a, 16b) or vice versa.

9. The displacement engine according to any one of the preceding claims, characterized in that the through opening (17) has a control geometry (19) arranged in the surface of the displacement spiral (13) that faces the counter spiral (14).

10. The displacement engine according to claim 9, characterized in that the control geometry (19) has a recess and / or an indentation.

11. The displacement engine according to claims 9 or 10, characterized in that the spiral sections (18) of the counter spiral (14) have a radially inner spiral wall (20a) and a radially outer spiral wall (20b), wherein the control geometry (19) and / or the through opening (17) is arranged between the spiral walls (20a, 20b) in a sealed state.

12. The displacement engine according to any one of the preceding claims, characterized in that the displacement spiral (13) and / or the counter spiral (14) at least sectionally have a chamfer (21).

13. A method for operating a displacement engine according to the spiral principle, in particular a scroll compressor, with a high-pressure chamber (11), a low-pressure chamber (12), an orbiting displacement spiral (13), a counter spiral (14), and a counter pressure chamber (15), which is arranged between the low-pressure chamber (12) and the displacement spiral (13), and wherein the displacement spiral (13) has at least one through opening (17) for fluidically connecting with the counter pressure chamber (15), in which the displacement spiral (13) engages into the counter spiral (14), such that at least a first and a second compression chamber (16a, 16b) temporarily receive a working medium, and the orbiting motion of the displacement spiral (13) during operation causes the through opening (17) to be at least sectionally temporarily arranged in the first compression chamber (16a), and subsequently at least sectionally temporarily arranged in the second compression chamber (16b), and connect the respective compression chamber (16a, 16b) in a fluid conducting manner with the counter pressure chamber (15), characterized in that the first compression chamber (16a) is connected in a fluid conducting manner with the counter pressure chamber (15) in an angular range of the rotation angle of the orbiting displacement spiral (13) of 120° to 400°, in particular of 247° to 367°.

14. A vehicle air conditioning system with a displacement engine, in particular with a scroll compressor, according to any one of claims 1 to 12.

15. A vehicle with a displacement engine according to any of claims 1 to 12 or a vehicle air conditioning system according to claim 14.