Displacement machine, method, vehicle air conditioning system, and vehicle

Abstract

The present invention relates to a displacement machine based on the spiral principle, in particular a scroll compressor, having a high-pressure chamber 11, a low-pressure chamber 12, an orbiting discharge spiral 13, a counter-spiral 14 and a back-pressure chamber 15, the back-pressure chamber being arranged between the low-pressure chamber 12 and the discharge spiral 113, an outlet opening 16 being arranged centrally in the counter-spiral 14 in the high-pressure region, through which the compressed working medium flows into the high-pressure chamber 11 during operation, and the discharge spiral 13 having at least one first and second passage openings 17a and 17b for fluid connection with the back-pressure chamber 15, the at least first passage opening 17a being arranged in the region of the outlet opening 16, so that the first passage opening 17a and the outlet opening 16 temporarily at least partially overlap each other during operation.

Description

[Technical field]

[0001] The present invention relates to a displacement machine based on the helical principle as defined in the preamble of claim 1. Furthermore, the invention relates to a method, a vehicle air conditioning system and a vehicle. [Background technology]

[0002] A displacement machine of the type mentioned at the outset is known from DE 10 2017105175 A1. This document describes a scroll compressor, which has a discharge helix and a counter helix. The discharge helix engages into the counter helix. By means of the orbiting discharge helix, compression chambers are formed in which the coolant is compressed. In order for the coolant to be compressed, the discharge helix must be in intimate contact with the counter helix. It is therefore advantageous if the discharge helix is ​​pressed against the counter helix. For this purpose, a back pressure chamber is arranged on the side of the discharge helix facing away from the counter helix. Back pressure chambers of this kind are also known under the name Back-Pressure-Raum. The back pressure chamber or counter pressure chamber has the function of building up pressure. For this purpose, the discharge helix has two openings, which fluidly connect the back pressure chamber or counter pressure chamber with the compression chamber. Pressure within the counter pressure chamber provides a force on the discharge spiral which presses it against the counter spiral so that the two spirals are sealed fluid-tight against each other.

[0003] In known scroll compressors of the type mentioned at the outset, the pressure in the back pressure chamber must be great enough to press the discharge helix against the counter helix so that the discharge helix abuts fluid-tightly against the counter helix, but this pressure must not be so great that friction occurs which would brake the orbital motion of the discharge helix or result in power losses.

[0004] Providing a sufficiently high pressure for the back pressure chamber in order to press the discharge spiral against the counter spiral and thus avoid as much power loss as possible is associated with constructional efforts and costs. [Prior art documents] [Patent documents]

[0005] [Patent Document 1] DE 102017105175 A1 Summary of the Invention [Problem to be solved by the invention]

[0006] It is therefore an object of the present invention to provide a displacement machine which improves the generation of pressure in a back pressure chamber for pressing the discharge spiral against the counter spiral, thereby allowing a simple and cost-effective construction of the displacement machine. It is further an object of the present invention to provide a method, a vehicle air conditioning system and a vehicle. [Means for solving the problem]

[0007] According to the invention, this problem is solved by: - for a displacement machine, according to the subject matter of claim 1, - in relation to the method, according to the subject matter of claim 12 - for vehicle air conditioning, by the subject matter of claim 13, and - in respect of the vehicle, the subject matter of claim 14 It will be resolved.

[0008] In particular, the problem is solved by a displacement machine, in particular a scroll compressor, based on the helical principle, which has a high pressure chamber, a low pressure chamber, an orbiting discharge helix, a counter helix and a back pressure chamber, the back pressure chamber being arranged between the low pressure chamber and the discharge helix, in which an outlet opening is arranged centrally in the counter helix in the high pressure region, through which the compressed working medium flows into the high pressure chamber during operation, and the discharge helix has at least a first and a second passage opening for fluid connection with the back pressure chamber, the at least first passage opening being arranged in the region of the outlet opening, so that during operation the first passage opening and the outlet opening temporarily at least partially overlap each other.

[0009] The high pressure chamber is the area into which the compressed working medium flows before being fed back into the circulation, for example into the cooling circulation.

[0010] The low pressure chamber may also be referred to as a suction chamber. From the low pressure chamber, gas flows radially outwardly between the counter spiral and the exhaust spiral.

[0011] The orbital motion of the discharge helix is ​​a motion on a circular locus.

[0012] The working medium is preferably a cooling fluid, particularly preferably a gaseous cooling fluid, for example CO2.

[0013] The outlet opening is arranged in the center or in the middle of the counter spiral, in other words in the area of ​​the midpoint of the counter spiral.

[0014] The outlet opening preferably has a valve, through which the working medium flows after compression into a high-pressure chamber, through which the working medium is again fed into the working circuit, in particular into the cooling circuit.

[0015] The first and second passage openings each form a fluid connection with a back pressure chamber.

[0016] At least the first passage opening is arranged in the region of the central outlet opening, the passage openings are arranged in the discharge spiral and the outlet opening in the counter spiral, so that the first passage opening is arranged opposite the outlet opening, whereby it is possible to arrange the first passage opening at least temporarily in the high pressure region.

[0017] The first passage opening and the outlet opening are arranged in parallel planes displaced relative to one another and temporarily at least partially overlap during operation of the compression machine, where overlapping means here that, when the two planes are viewed from above, the first passage opening is tangent, intersects and / or touches the outer contour of the outlet opening.

[0018] In other words, overlapping means that when parallel planes are superimposed, the first passage opening and the outlet opening have at least one common intersection point at at least one time during the movement of the discharge spiral.

[0019] This has the advantage that a sufficiently large pressure can be generated in the back pressure chamber to press the discharge spiral against the counter spiral.

[0020] Since the first passage opening and the outlet opening temporarily at least partially overlap, the first passage opening remains in the high pressure region over as large an angular region of the rotation angle of the discharge spiral as possible and thus for as long a period as possible and forms a fluid connection with the back pressure chamber.

[0021] By means of the fluid connection, a pressure is generated in the back pressure chamber, the pressure for pressing the discharge spiral against the counter spiral being adapted by temporarily locating the first through opening in the region of the outlet opening in such a way that the friction forces which brake the orbital movement of the discharge spiral and lead to power losses are as small as possible and at the same time the discharge spiral is located sufficiently fluid-tight on the counter spiral.

[0022] Furthermore, by means of the two through openings a continuous fluid connection with the back pressure chamber is possible, i.e. further fluid connections with the back pressure chamber can be omitted, which allows for a more compact and more cost-effective construction shape of the displacement machine.

[0023] Preferred embodiments of the invention are set forth in the subclaims.

[0024] In a particularly preferred embodiment, the second passage opening is arranged in a region of the discharge spiral which, during operation, has a lower pressure than in the high-pressure region.

[0025] It is thereby possible to provide a high pressure to the back pressure chamber, for example if the compressed working medium in the compression chamber exerts a high force on the discharge spiral in the direction of the counter spiral, or if the pressure provided by the compressed working medium to the compression spiral is low, the pressure in the back pressure chamber can also be adjusted low in order to minimize power losses.

[0026] In another particularly preferred embodiment, the first passage opening is connected in a fluid-guiding manner to the backpressure chamber within an angular region of the orbiting discharge helix having a rotation angle of between 435° and 650°.

[0027] The angular range of the rotation angle, in which the first through opening is fluidly connected with the back pressure chamber, is advantageous because it allows a fluid connection between the back pressure chamber and the compression chamber over as large a range as possible of the rotation angle of the orbiting discharge spiral. Furthermore, since the compression of the working medium and therefore the pressure is higher with a larger rotation angle, a sufficiently high pressure can be provided in the back pressure chamber.

[0028] In a preferred embodiment, the first passage opening has a temporary overlap with the outlet opening of between 1% and 100%, in particular between 10% and 90%, in particular between 20% and 80%, in particular between 30% and 70%, in particular between 40% and 60%.

[0029] By the largest possible overlap, the first passage opening is located in the high pressure area of ​​the displacement machine for as long as possible, which allows a period of favorable length during which the passage opening is open. By various degrees of overlap, the period during which the first passage opening and the outlet opening overlap can be adapted.

[0030] In another preferred embodiment, during operation at least a first and a second compression chamber for receiving the working medium are formed temporarily and the second passage opening is arranged in the discharge helix, so that by the orbital movement of the discharge helix during operation the second passage opening is temporarily at least partially located in the first compression chamber and then temporarily at least partially located in the second compression chamber.

[0031] The back pressure chamber is thereby additionally temporarily fluidly connected alternately with the first compression chamber and then with the second compression chamber by means of the second passage opening, thereby making it possible for the back pressure chamber to be fluidly connected with at least one of the compression chambers and / or with the high pressure region in the region of the outlet.

[0032] It is particularly advantageous if the second passage opening is arranged in the first compression chamber within an angular range of 95°-250° of the rotation angle of the orbiting discharge spiral and in the second compression chamber within an angular range of 285°-650°.

[0033] The angular region of the rotation angle, in which the second passage opening is temporarily arranged in the first compression chamber and in the second compression chamber, is effective, since thereby the second passage opening is fluidly connected with the back pressure chamber for as long as possible.

[0034] Furthermore, at larger rotation angles, compression in the compression chambers progresses, as a result of which a higher pressure can be applied to the backpressure chamber than at smaller rotation angles, in other words, the passage opening is only located in the first or second compression chamber at a rotation angle at which the pressure in the compression chamber is sufficiently high to generate sufficient pressure in the backpressure chamber and to press the discharge spiral against the counter spiral in a fluid-tight manner and with little power loss.

[0035] It is advantageous if the first and / or the second passage opening is arranged in the bottom section of the discharge spiral, since this facilitates the passage of the counter spiral by the passage opening.

[0036] Furthermore, a straight and as short as possible connection to the back pressure chamber can thus be realised.

[0037] Advantageously, the first passage opening has a smaller diameter than the second passage opening, the diameters being between 0.1 mm and 1 mm.

[0038] It is particularly advantageous if the first passage opening has a diameter of 0.3 mm and / or if the second passage opening has a diameter of 0.5 mm.

[0039] Due to the different diameters, the first and second passage openings can be adapted to the pressure in the compression chamber. In the radially inner region of the nested spirals, the degree of compression and therefore the pressure of the working medium is higher than in the radially outer region of the nested spirals. The first passage opening is arranged in the radially inner region of the discharge spiral, which has a higher degree of compression. The second passage opening is preferably arranged in the radially outer region, which has a lower degree of compression than in the radially inner region. The diameter of the first passage opening is smaller and thereby throttles the fluid flow from the region with a higher degree of compression or from the high pressure region into the back pressure chamber. In the radially outer region, the pressure is lower and therefore the larger diameter of the second passage opening is effective to provide sufficient pressure to the back pressure chamber, thereby pressing the discharge spiral against the counter spiral.

[0040] In a preferred embodiment, the first passage opening and / or the second passage opening has a circular, elliptical or oval cross section.

[0041] This allows for various preferred configurations of the passage openings, which influence the flow properties of the working medium. For example, it is possible for the area of ​​the first passage opening, which is initially exposed when passing through the counter-spiral during operation, to have a larger cross-section than the area still covered by the counter-spiral, so that a sufficient fluid connection with the back pressure chamber is formed even before the passage opening is completely opened.

[0042] In a preferred embodiment, the ejection spiral and / or the counter spiral are at least partially chamfered.

[0043] By means of the chamfer it is possible to reduce the area of ​​the rotation angle through which the first and / or the second passage opening moves to pass through the counter spiral, i.e. the chamfer makes it possible to shorten the period during which the passage openings are closed.

[0044] Within the framework of the present invention, a method for driving a displacement machine is disclosed and claimed, in which during operation of the displacement machine, a first passage opening temporarily at least partially overlaps with an outlet opening centrally arranged in the counter spiral and a fluid connection with a back pressure chamber is formed.

[0045] Furthermore, within the scope of the invention, a vehicle air conditioning system and a vehicle having a vehicle air conditioning system are disclosed and claimed.

[0046] The invention will now be described in detail by way of examples with reference to the accompanying drawings, in which: [Brief description of the drawings]

[0047] [Figure 1] FIG. 1 shows a cross section of an embodiment according to the invention of a displacement machine. [Diagram 2] FIG. 2 shows another cross section of the displacement machine shown in FIG. [Diagram 3] FIG. 3 shows a schematic cross-section of the counter spiral and the discharge spiral of an embodiment of the displacement machine according to the invention. [Figure 4] FIG. 4 shows a schematic cross section of the counter spiral and the discharge spiral of an embodiment of the displacement machine according to the invention at a rotation angle of 0° during the compression cycle. [Diagram 5] FIG. 5 shows a schematic cross-section of the displacement machine shown in FIG. 4 at a rotation angle of 120°. [Figure 6] FIG. 6 shows a schematic cross-section of the displacement machine shown in FIG. 4 at a rotation angle of 260°. [Figure 7] FIG. 7 shows a schematic cross-section of the displacement machine shown in FIG. 4 through a rotation angle of 360°. [Figure 8] FIG. 8 shows a schematic cross-section of the displacement machine shown in FIG. 4 at a rotation angle of 460°. [Figure 9] FIG. 9 shows a schematic cross-section of the displacement machine shown in FIG. 4 at a rotation angle of 500°. [Figure 10]FIG. 10 shows a schematic cross section of the displacement machine shown in FIG. 4 at a rotation angle of 600°. [Figure 11] FIG. 11 shows a schematic cross-section of the displacement machine shown in FIG. 4 at a rotation angle of 720°. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0048] 1 and 2 each show, in cross section, an embodiment according to the invention of a displacement machine 10, as may be used, for example, in a vehicle air conditioning system.

[0049] The displacement machine 10 has a housing 19. The housing 19 has a cylindrical shape. A drive 20 is arranged in the housing 19. The drive 20 can be, for example, an electric motor or a mechanical drive. The drive 20 is connected to a shaft 21.

[0050] The shaft 21 extends in the longitudinal direction of the housing 19. An eccentric bearing 22 with an eccentric pin 23 is arranged at one axial end of the shaft 21. The discharge spiral 13 is connected to the shaft 21 by means of this eccentric bearing 22.

[0051] A counter spiral 14 is arranged in the housing 19 on the side of the discharge spiral 13 facing away from the eccentric bearing 22. The counter spiral 14 is arranged stationary and immovable in the housing 19 of the displacement machine 10. It is also possible for the counter spiral 14 to be formed integrally with the housing 19.

[0052] A high pressure chamber 11 is arranged on the side of the counter spiral 14 opposite the discharge spiral.

[0053] An outlet opening 16 is arranged centrally in the counter spiral 14. The outlet opening 16 extends between the high pressure chamber and the side of the counter spiral 14 facing towards the discharge spiral 13.

[0054] A low pressure chamber 12 is arranged on the opposite side of the discharge spiral 13 from the counter spiral 14. Between the low pressure chamber 12 and the discharge spiral 13 a back pressure chamber 15 is arranged.

[0055] The discharge spiral 13 is arranged in the housing 19 so as to be movable in a direction parallel to the longitudinal direction of the axis 21. In other words, the discharge spiral 13 is slidable towards and away from the counter spiral 14. In Fig. 2 it can be seen that in the bottom of the discharge spiral 13 a first through-opening 17a and a second through-opening 17b are arranged.

[0056] The first through opening 17a is arranged in the radially inner region of the discharge spiral 13. The second through opening 17b is arranged in the radially outer region of the discharge spiral 13. The first through opening 17a and the second through opening 17b extend perpendicular to the surface of the bottom. In the installed state, the through openings 17a, 17b are arranged between the side of the bottom facing towards the counter spiral 14 and the side of the bottom facing away from the counter spiral 14.

[0057] The through openings 17a, 17b have openings on both sides of the bottom, which openings connect the two sides of the bottom with each other, in other words, the through openings 17 form a passage between the two sides of the bottom of the discharge spiral 13. The through openings 17a, 17b form a fluid connection with the back pressure chamber 15.

[0058] The passage openings 17a, 17b have a circular cross section. Other shapes are also possible, for example elliptical, oval or polygonal. The passage openings 17a, 17b preferably have holes. The diameter of the passage openings 17a, 17b is preferably between 0.1 mm and 1 mm. In particular, the diameter of the first passage opening 17a is 0.3 mm and the diameter of the second passage opening 17b is 0.5 mm.

[0059] FIG. 3 is a schematic representation of a discharge spiral 13 and a counter spiral 14 as may be used in the displacement machine 10 shown in FIGS.

[0060] The discharge helix 13 and the counter helix 14 each have a helical section 24 and a base. These helical sections 24 are arranged perpendicularly on the bases of the discharge helix 13 and the counter helix 14, respectively. The helical sections 24 have a helical or screw-shaped geometry. In the assembled state, the helical section 24 of the discharge helix 13 extends towards the counter helix 14, and the helical section 24 of the counter helix 14 extends towards the discharge helix 13. The helical sections 24 of the discharge helix 13 and the counter helix 14 engage with each other. During operation, the helical sections 24 are in contact with the bases of the opposing helical sections 13, 14, respectively.

[0061] Compression chambers 18a, 18b are formed by the nesting spirals 13, 14. In other words, the compression chambers 18a, 18b are bounded by the spiral sections 24 of the discharge spiral 13 and the counter spiral 14.

[0062] The outlet opening 16 is arranged centrally and eccentrically in the counter spiral 14. In addition to the outlet opening 16, two secondary outlet openings 25a, 25b are arranged in the counter spiral 14. The secondary outlet openings 25a, 25b can also be called pre-outlets. The secondary outlet openings 25a, 25b are radially spaced from the center of the counter spiral 14.

[0063] An inner compression chamber 26 is arranged in the radially inner region of the two nested spirals 13, 14. The expression "centrally or centrally arranged" in the line of sight to the outlet opening therefore means that the outlet opening at least partially and temporarily intersects the inner compression chamber 26 defined by the discharge spiral 13 and the counter spiral 14.

[0064] In figures 4 to 11, various states of the compression cycle of the displacement machine 10 are shown. In the following, the relative positions of the discharge spiral 13 and the counter spiral 14 with respect to each other are described as a snapshot of the geometric arrangement of the respective components and their functions or actions. The spiral arrangement shown in figures 4 to 11 corresponds substantially structurally to the spiral arrangement shown in figure 3.

[0065] A compression cycle is one pass or period of the compression process that is continuously repeated.

[0066] The position of the discharge helix 13 during the compression cycle can be indicated by the rotation angle of the orbital motion. The rotation angle of the discharge helix 13 in Figure 4 is 0°.

[0067] In Fig. 4, a first compression chamber 18a and a second compression chamber 18b are formed in the radially outer region. The two compression chambers 18a, 18b are closed.

[0068] When the compression chamber 18 is surrounded in a fluid-tight manner by the discharge helix 13 and the helical section 24 of the counter helix 14, the compression chamber 18 is closed.

[0069] Further first and second compression chambers 18c, 18d are arranged in the radially inner regions of the spirals 13, 14, respectively, which have a smaller relative volume than the compression chambers 18a, 18b, respectively.

[0070] The relative volume of the compression chamber 18 is the variable volume of the compression chamber at a given point during the compression cycle of the displacement machine 10 relative to the initial volume of the compression chamber 18 at a rotation angle of 0°.

[0071] The first passage opening 17a is covered by the helical section 24 of the counter helix 14. The second passage opening 17b is located in the second compression chamber 18d. The first passage opening 17a is therefore closed and the second passage opening 17b is open. Thereby, there is a fluid connection between the second compression chamber 18b and the back pressure chamber 15, and the discharge helix 13 is pressed against the counter helix 14.

[0072] A snapshot at 120° of rotation is shown in Figure 5. The compression chambers 18a, 18b have moved radially inwards. The relative volumes of the compression chambers 18a, 18b have decreased.

[0073] The relative volumes of the compression chambers 18a, 18b decrease with increasing rotation angle. The decrease in relative volume causes the pressure in the compression chambers 18a, 18b to increase.

[0074] The compression chambers 18c, 18d are joined together as an inner compression chamber 26. The inner compression chamber 26 preferably corresponds to a high pressure region, in which the first passage opening 17a is arranged.

[0075] The first passage opening 17a is arranged in the inner compression chamber 26 or in the high pressure region. The first passage opening 17a intersects with the outlet opening 16. The second passage opening 17b is arranged in the first compression chamber 18a. The two passage openings 17a, 17b are thus open and thus allow a fluid connection with the back pressure chamber 15.

[0076] The concept of "intersecting" means that the two openings 17a, 16 are arranged at least partially overlapping each other. The first passage opening 17a has a distance to the outlet opening 16 in the direction of the counter-spiral 14. In other words, the passage opening 17a at least partially covers, passes through and / or crosses the outlet opening 16.

[0077] The partial intersection of the through openings 17a allows the highest possible pressure to be created in the back pressure chamber 15. This further provides that the back pressure chamber 15 is in fluid connection with the high pressure region for the longest possible period or for a large rotation angle region.

[0078] FIG. 6 shows the compression cycle at a rotation angle of 260°.

[0079] The first and second compression chambers 18a, 18b have moved further radially inward. The relative volumes of the inner compression chamber 26 and the first and second compression chambers 18a, 18b have decreased. Thus, the pressure in the compression chambers 18a, 18b has increased further.

[0080] The first through opening 17a is furthermore arranged in the inner compression chamber 26. The first through opening 17a no longer overlaps with the outlet opening 16. The second through opening 17b is covered by the helical section 24 of the counter helix 14. The pressure in the back pressure chamber 15 is provided in FIG. 6 by the fluid connection of the through opening 17a with the inner compression chamber.

[0081] FIG. 7 shows snapshots of a compression cycle through a 360° rotation angle.

[0082] In the radially outer region of the discharge spiral 13 and the counter spiral 14, two new compression chambers 18e, 18f are formed.

[0083] The first compression chamber 18a and the second compression chamber 18b have been moved further towards the center or exit opening 16. The relative volume of the inner compression chamber 26 has been further reduced. The exit opening 16 is now partially disposed within the inner compression chamber 26. In other words, the cross-sectional area of ​​the inner compression chamber 26 is smaller than the cross-sectional area of ​​the exit opening 16.

[0084] The first passage opening 17a is covered by the helical section 24 of the counter helix 14 and is therefore closed. The second passage opening 17b is located in the second compression chamber 18b after the passage of the helical section 24 and is open.

[0085] FIG. 8 shows a snapshot at a rotation angle of 460°.

[0086] The compression chambers 18e, 18f have moved further towards the outlet 16. The relative volumes of the compression chambers 18e, 18f have further decreased.

[0087] The inner compression chamber 26 created by the combination of the first compression chamber 18c and the second compression chamber 18d has disappeared. The first compression chamber 18a and the second compression chamber 18b have combined to form the new inner compression chamber 26.

[0088] A first passage opening 17a is located in the inner compression chamber 26. The first passage opening 17a overlaps with the outlet opening 16. The second passage opening 17b is partially covered by the helical section 24 of the counter helix 14, which helical section extends between the first compression chamber 18c and the inner compression chamber 26. The second passage opening 17b is partially open.

[0089] The first through opening 17a provides a fluid connection with the high pressure area or inner compression chamber 26 and the back pressure chamber 15. Here it effectively acts on the pressure in the back pressure chamber 15, since the second through opening 17b is not yet fully opened, but only partially opened, so that at this point in the compression cycle a lower pressure would result without the first through opening.

[0090] FIG. 9 shows a snapshot of the compression cycle at 500°.

[0091] The relative volumes of compression chambers 18e, 18f and inner compression chamber 26 are further reduced.

[0092] The outlet opening 16 is located completely in the inner compression chamber 26. The first passage opening 17a is also located in the inner compression chamber 26 and overlaps with the outlet opening 16. The second passage opening 17b is no longer located partially but completely in the first compression chamber 18e. The two passage openings 17a, 17b are open and are fluidly connected with the back pressure chamber 15.

[0093] 10, where the rotation angle is 600°, the outlet opening 16 is furthermore arranged in the inner compression chamber 26. The first through opening 17a does not overlap with the outlet opening 16.

[0094] The second passage opening 17b is arranged in the first compression chamber 18e. The second passage opening 17b abuts tangentially on the helical section 24.

[0095] FIG. 11 shows a state of the compression cycle that corresponds to a state at a rotation angle of substantially 360° (see FIG. 7), in which the compression chamber 26 in FIG. 11 arises from the compression chambers 18a, 18b, as opposed to the state shown in FIG. 7.

[0096] A shaft 21 is operatively connected to the drive 20. During driving, the rotation of the shaft 21 and the eccentric coupling of the shaft 21 with the discharge spiral 13 results in an orbital movement of the discharge spiral 13.

[0097] A working medium, e.g., coolant, is drawn from the low pressure chamber 12 into the radially outer region of the helices 13, 14 at the start of a compression cycle. The working medium is transferred into the compression chamber 18 between the discharge helix 13 and the counter helix 14. The orbiting movement of the discharge helix 13 reduces the relative volume of the compression chamber 8 in order to compress the working medium.

[0098] The compression chambers 18 are eliminated in the course of the compression cycle. In other words, the compression chambers 18 are temporary. They are repeatedly formed anew during the drive in the outer radial area of ​​the helical arrangement and then move radially inwards in the helical arrangement. The path of movement of the compression chambers 18 is helical. In the radial interior of the helical sections 13, 14, the first compression chamber 18a and the second compression chamber 18b first merge into the inner compression chamber 26. The relative volume of the inner compression chamber 26 gradually decreases until the inner compression chamber 26 is eliminated. Immediately afterwards, a new inner compression chamber 26 is formed by the next two first compression chambers 18c and the second compression chamber 18d.

[0099] From the inner compression chamber 26 , the compressed working medium flows through the outlet opening 16 into the high pressure chamber 11 .

[0100] 4-11, up to five compression chambers 18, 26 are possible: two pairs each having a first compression chamber 18a and a second compression chamber 18b, and an inner compression chamber 26. Additionally, configurations having more or fewer compression chambers 18, 26 are also possible.

[0101] The through openings 17a, 17b move on a circular path due to the orbital movement of the discharge spiral 13. The through openings 17a, 17b make it possible to fluidly connect the compression chambers 18, 26 with the back pressure chamber 15 in order to provide sufficient pressure to the discharge spiral 13 during operation and thereby press it against the counter spiral 14.

[0102] Within the compression cycle, the passage openings 17a, 17b are preferably open in the following angular regions: the first passage opening 17a forms a fluid connection between the inner compression chamber 26 and the back pressure chamber 15 within an angular region of rotation angles between 435° and 650°; the second passage opening 17b forms a fluid connection with the first compression chamber 18a and the back pressure chamber 15 within an angular region of rotation angles between 95° and 250°; the second passage opening 17b is located in the second compression chamber 18b within an angular region of rotation angles between 285° and 650°; the second passage opening 17b is covered by the helical section 24 of the counter helix 14 within an angular region of rotation angles between 250° and 285°. However, it does not necessarily have to be the case that the first passage opening 17a is open when the second passage opening 17b is covered by the counter helix, or vice versa. In the snapshot shown in Fig. 6 at a rotation angle of 260°, the second passage opening 17b is closed. However, the preceding compression cycle is not yet completed. The rotation angle position of the preceding compression cycle corresponds to approximately 620° in Fig. 6. The first passage opening 17a is therefore located in the inner compression chamber 26, thereby allowing a fluid connection with the back pressure chamber 15.

[0103] The second passage opening 17b is located first in the first compression chamber 18a and then in the second compression chamber 18b of a compression cycle during operation of the displacement machine 10. The second passage opening 17b is located in one of the compression chambers 18a, 18b once each compression cycle. After the second compression chamber 18b, the second passage opening 17b moves to the first compression chamber 18c of the following compression cycle.

[0104] Through the through openings 17a, 17b, part of the working medium flows into the back pressure chamber 15. The pressure in the back pressure chamber 15 increases as a result. This pressure provides an axial force to the discharge spiral 13, which acts in the direction of the counter spiral 14. The discharge spiral 13 is axially movable so that it is pressed against the counter spiral 14. The pressing of the discharge spiral 13 against the counter spiral 14 results in a compression of the working medium with as little power loss as possible.

[0105] In the embodiment shown in Figures 4 to 11, multiple compression cycles are performed simultaneously with a time stagger. The first compression chamber 18a and the second compression chamber 18b, and the first compression chamber 18c and the second compression chamber 18d are associated with different compression cycles. In other words, each compression cycle has a pair of the first compression chamber 18a and the second compression chamber 18b. The present disclosure also includes the following inventions. The first aspect is A displacement machine based on the helical principle, in particular a scroll compressor, comprising a high pressure chamber (11), a low pressure chamber (12), the orbiting discharge helix (13), a counter helix (14) and a back pressure chamber (15), the back pressure chamber being arranged between the low pressure chamber (12) and the discharge helix (13), an outlet opening (16) being arranged in the counter helix (14) in the high pressure region, through which the working medium compressed during operation flows into the high pressure chamber (11), and the discharge helix (13) has at least one first through opening (17a) and a second through opening (17b) for fluid connection with the back pressure chamber (15), The displacement machine is characterized in that the at least one first passage opening (17a) is arranged in the area of ​​the outlet opening (16) so that during operation the first passage opening (17a) and the outlet opening (16) temporarily at least partially overlap. The second aspect is A displacement machine in a first aspect, characterized in that the second passage opening (17b) is arranged in a region of the discharge spiral (13), said region having a lower pressure during operation than the pressure in the high pressure region. The third aspect is The displacement machine according to the first or second aspect, characterized in that the first passage opening (17a) is connected to the back pressure chamber (15) in a fluid-guiding manner within an angular range of a rotation angle of 435° to 650° of the orbiting discharge spiral (13). The fourth aspect is A displacement machine according to any one of the first to third aspects, characterized in that the first passage opening (17a) has a temporary overlap with the outlet opening (16) of between 1% and 100%, in particular between 10% and 90%, in particular between 20% and 80%, in particular between 30% and 70%, in particular between 40% and 60%. The fifth aspect is The displacement machine according to any one of the first to fourth aspects, characterized in that during operation at least one first compression chamber (18a) and one second compression chamber (18b) are temporarily formed to accommodate a working medium and the second passage opening (17b) is arranged in the discharge spiral (13), so that during operation, due to the orbital movement of the discharge spiral (13), the second passage opening (17b) is temporarily at least partially arranged in the first compression chamber (18a) and then temporarily at least partially in the second compression chamber (18b). The sixth aspect is A displacement machine according to a fifth aspect, characterized in that the second passage opening (17b) is arranged in the first compression chamber (18a) within an angular range of a rotation angle of the orbiting discharge spiral (13) between 95° and 250°, and in the second compression chamber (18b) within an angular range of 285° and 650°. The seventh aspect is A displacement machine according to any one of the first to sixth aspects, characterized in that the first passage opening (17a) and / or the second passage opening (17b) are arranged in a bottom section of the discharge spiral (13). The eighth aspect is The displacement machine according to any one of the first to seventh aspects, characterized in that the first passage opening (17a) and / or the second passage opening (17b) have a circular, elliptical or egg-shaped cross-section. The ninth aspect is A displacement machine according to any one of the first to eighth aspects, characterized in that the first passage opening (17a) has a smaller diameter than the second passage opening (17b), and the diameters of the first passage opening (17a) and the second passage opening (17b) are between 0.1 mm and 1 mm. A tenth aspect is A displacement machine according to any one of the first to ninth aspects, characterized in that the first passage opening (17a) has a diameter of 0.3 mm and / or the second passage opening (17b) has a diameter of 0.5 mm. An eleventh aspect is A displacement machine according to any one of the first to tenth aspects, characterized in that the discharge spiral portion (13) and / or the counter spiral portion (14) have at least partially chamfered portions. A twelfth aspect is In the method for driving a displacement machine according to any one of the first to eleventh aspects, During operation of the displacement machine (10), the first passage opening (17a) temporarily at least partially overlaps with the outlet opening (16) centrally located in the counter spiral (14) and a fluid connection with the back pressure chamber (15) is formed. A thirteenth aspect is A vehicle air conditioning system having the displacement machine according to any one of the first to eleventh aspects, in particular having a scroll compressor. A fourteenth aspect is A vehicle having the displacement machine according to any one of the first to eleventh aspects or the vehicle air conditioning system according to the thirteenth aspect. [Explanation of symbols]

[0106] 10. Pushing Machine 11. High Pressure Chamber 12 Low Pressure Chamber 13 Discharge spiral part 14 Counter Spiral Section 15 Back Pressure Chamber 16 Outlet opening 17a First passage opening 17b Second passage opening 18a First compression chamber 18b Second compression chamber 18c First compression chamber 18d Second Compression Chamber 18e First compression chamber 18f Second Compression Chamber 19 Housing 20 Drive 21 Axis 22 Eccentric bearing 23 Eccentric pin 24 Spiral Section 25a Secondary exit opening 25b Secondary exit opening 26 Inner Compression Chamber

Claims

1. A displacement machine based on the helical principle, comprising a high pressure chamber (11), a low pressure chamber (12), an orbiting discharge helix (13), a counter helix (14) and a back pressure chamber (15), the back pressure chamber being arranged between the low pressure chamber (12) and the discharge helix (13), an outlet opening (16) being arranged in the counter helix (14) in a high pressure region, through which the working medium compressed during operation flows into the high pressure chamber (11), and the discharge helix (13) has at least one first through opening (17a) and a second through opening (17b) for fluid connection with the back pressure chamber (15), the at least one first passage opening (17a) is arranged in the region of the outlet opening (16) so that during operation the first passage opening (17a) and the outlet opening (16) temporarily at least partially overlap, 13. A displacement machine, characterized in that the first passage opening (17a) is in a fluid-guiding connection with the back pressure chamber (15) within an angular range of a rotation angle of the orbiting discharge spiral (13) between 435° and 650°.

2. 2. A displacement machine according to claim 1, characterized in that the second passage opening (17b) is arranged in a region of the discharge spiral (13), which region has a lower pressure during operation than the pressure in the high-pressure region.

3. 3. A displacement machine according to claim 1 or 2, characterized in that the first passage opening (17a) has a temporary overlap with the outlet opening (16) of between 1% and 100%.

4. 4. The displacement machine according to claim 1, characterized in that during operation, at least one first compression chamber (18a) and at least one second compression chamber (18b) are temporarily configured to receive a working medium and the second passage opening (17b) is arranged in the discharge spiral (13), so that during operation, the orbital movement of the discharge spiral (13) causes the second passage opening (17b) to be temporarily at least partially located in the first compression chamber (18a) and then temporarily at least partially located in the second compression chamber (18b).

5. 5. The displacement machine according to claim 4, characterized in that the second passage opening (17b) is arranged in the first compression chamber (18a) within an angular range of 95° to 250° of the rotation angle of the orbiting discharge spiral (13) and in the second compression chamber (18b) within an angular range of 285° to 650°.

6. 6. The displacement machine according to claim 1, characterized in that the first passage opening (17a) and / or the second passage opening (17b) are arranged in the bottom section of the discharge spiral (13).

7. 7. A displacement machine according to claim 1, characterized in that the first passage opening (17a) and / or the second passage opening (17b) have a circular, elliptical or oval cross section.

8. A displacement machine according to any one of the preceding claims, characterized in that the first passage opening (17a) has a smaller diameter than the second passage opening (17b), their diameters being between 0.1 mm and 1 mm.

9. 9. A displacement machine according to any one of the preceding claims, characterized in that the first passage opening (17a) has a diameter of 0.3 mm and / or the second passage opening (17b) has a diameter of 0.5 mm.

10. 10. A displacement machine according to any one of the preceding claims, characterized in that the discharge spiral (13) and / or the counter spiral (14) at least partially have a chamfer.

11. A method for driving a displacement machine according to any one of claims 1 to 10, comprising the steps of: During operation of the displacement machine (10), the first passage opening (17a) temporarily at least partially overlaps with a centrally located outlet opening (16) in the counter spiral (14) and a fluid connection with the back pressure chamber (15) is formed.

12. A vehicle air conditioning installation comprising a displacement machine according to any one of the preceding claims.

13. A vehicle comprising a displacement machine according to any one of claims 1 to 10 or a vehicle air conditioning system according to claim 12.

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