Positive displacement machine, method, vehicle air conditioning system and vehicle

Abstract

The invention relates to a volumetric machine based on the screw principle, in particular a scroll compressor, having a high-pressure chamber (11), a low-pressure chamber (12), a orbiting volumetric screw (13), a counter-screw (14) and a counter-pressure chamber (15) arranged between the low-pressure chamber (12) and the volumetric screw (13), wherein in the counter-screw (14) a discharge opening (16) is centrally arranged in a high-pressure region, through which in operation the compressed working medium flows into the high-pressure chamber (11), and wherein the volumetric screw (13) has at least a first and a second through-hole (17a, 17b) for fluid communication with the counter-pressure chamber (15), wherein at least the first through-hole (17a) is arranged in the region of the discharge opening (16) such that in operation the first through-hole (17a) and the discharge opening (16) temporarily at least partially overlap.

Description

Technical Field

[0001] This invention relates to a volumetric machine (Verdrängermaschine) based on the spiral principle as described in the preamble of claim 1. Furthermore, this invention also relates to methods, vehicle air conditioning systems, and vehicles. Background Technology

[0002] The aforementioned type of positive displacement machine is known from DE 10 2017 105 175 B3. DE 10 2017 105175 B3 describes a scroll compressor comprising a positive displacement screw and a reverse screw. The positive displacement screw and the reverse screw are engaged. A compression chamber is formed by the rotating positive displacement screw, in which the coolant is compressed. In order to compress the coolant, the positive displacement screw must abut against the reverse screw. Therefore, it is advantageous to press the positive displacement screw against the reverse screw. For this purpose, a back pressure chamber is provided on the side of the positive displacement screw opposite to the reverse screw. This back pressure chamber is also called a back pressure space. The back pressure chamber or back pressure space has the function of establishing pressure. For this purpose, the positive displacement screw includes two openings that fluidly communicate the back pressure chamber or back pressure space with the compression chamber. The pressure in the back pressure space applies a force to the volumetric screw, which presses the volumetric screw against the anti-screw, so that the two screws are sealed to each other in a fluid-tight manner.

[0003] In the known types of scroll compressors mentioned at the beginning, the pressure in the back pressure chamber must be high enough to press the positive displacement screw against the reverse screw, so that the positive displacement screw is fluid-tightly pressed against the reverse screw. However, the pressure should not be too high to avoid frictional forces that slow down the rotation of the positive displacement screw or cause performance loss.

[0004] Providing the counter-pressure chamber with sufficiently high pressure to press the volumetric spiral against the counter-spiral component, thereby minimizing performance loss, is a design-related task. Summary of the Invention

[0005] Therefore, the object of the present invention is to provide a volumetric machine in which the pressure in the counter-pressure chamber for pressing the volumetric auger against the counter-auger is improved, making a simple and low-cost structure of the volumetric machine possible. Furthermore, the object of the present invention is also to provide a method, a vehicle air conditioning system, and a vehicle.

[0006] According to the present invention: - The task concerning volumetric machines is solved by the volumetric machine based on the spiral principle of this invention. - The task regarding the method is solved by the method of the present invention for operating a volumetric machine based on the helical principle. - The task concerning the vehicle air conditioning system is solved by the vehicle air conditioning system of the present invention, and - The task concerning transportation is solved by the transportation of the present invention.

[0007] Specifically, the objective is achieved through a positive displacement machine based on the helical principle, particularly a scroll compressor, which has a high-pressure chamber, a low-pressure chamber, a rotating positive displacement helical component, a reverse helical component, and a counter-pressure chamber arranged between the low-pressure chamber and the positive displacement helical component. In the reverse helical component, the outlet is centrally located in the high-pressure region through which the compressed working medium flows into the high-pressure chamber during operation. The positive displacement helical component has at least a first through-hole and a second through-hole for fluid communication with the counter-pressure chamber, wherein at least the first through-hole is arranged in the region of the outlet such that during operation, the first through-hole and the outlet at least partially overlap temporarily.

[0008] The high-pressure chamber is the area in which the compressed working medium flows in before being fed into the circuit (e.g., cooling circuit).

[0009] The low-pressure chamber can also be called the suction space. Gas exiting the low-pressure chamber flows radially outward between the anti-spiral component and the volumetric spiral component.

[0010] The rotational motion of a volumetric screw component refers to its motion along a circular path.

[0011] The working medium is preferably a cooling fluid, and more preferably a gaseous cooling fluid, such as CO2.

[0012] The outlet is centrally located within the anti-spiral component. In other words, the outlet is located within the area of ​​the center point of the anti-spiral component.

[0013] Preferably, the outlet has a valve. The working medium, after compression, flows into the high-pressure chamber through the outlet. The working medium is then fed back into the working circuit, particularly the cooling circuit, via the high-pressure chamber.

[0014] The first and second through holes each establish fluid communication with the back pressure chamber.

[0015] At least the first through-hole is arranged in the region of the central outlet. The through-hole is arranged in the volumetric spiral member, while the outlet is arranged in the anti-spiral member. Therefore, the first through-hole and the outlet are arranged opposite each other. This allows the first through-hole to be arranged, at least temporarily, in the high-pressure region.

[0016] The first through-hole and the outlet are arranged in parallel planes that are staggered from each other, and at least partially overlap temporarily during operation of the volumetric machine. Here, "overlap" means that in the top view of the two planes, the outer contours of the first through-hole and the outlet are tangent to, intersect with, and / or contact each other.

[0017] In other words, "overlap" means that when parallel planes overlap vertically, the first through hole and the outlet have at least one common intersection point at at least one time point during the operation of the volumetric screw.

[0018] This allows for the generation of pressure in the counter-pressure chamber large enough to press the volumetric screw against the counter-screw.

[0019] Because the first through-hole and the outlet overlap at least partially and temporarily, the first through-hole remains in the high-pressure region and establishes fluid communication with the back pressure chamber for as long as possible within the largest possible range of rotation angles of the volumetric screw.

[0020] Pressure is generated in the counter-pressure chamber through fluid communication. The pressure pressing the volumetric auger against the counter-auger is adjusted through a first through-hole temporarily positioned in the outlet area, so that the rotational motion of the volumetric auger and the frictional force causing performance loss are minimized, while the volumetric auger is positioned on the counter-auger in a sufficiently fluid-tight manner.

[0021] Furthermore, continuous fluid communication with the back pressure chamber can be achieved through two through-holes. Therefore, other fluid communication with the back pressure chamber can be eliminated. This allows for a more compact configuration and lower cost for the positive displacement machine.

[0022] Preferred embodiments of the present invention are described in the dependent claims.

[0023] In a particularly preferred embodiment, the second through-hole is arranged in the region of the volumetric spiral member, which has a lower pressure during operation than the pressure in the high-pressure region.

[0024] This allows high pressure to be applied to the counter-pressure chamber, for example, when the compressed working medium in the compression chamber applies a large force to the volumetric screw in the direction of the counter-pressure chamber. If the pressure applied to the volumetric screw by the compressed working medium is low, the pressure in the counter-pressure chamber can also be set low to minimize performance loss.

[0025] In another particularly preferred embodiment, the first through hole is fluid-guided to the back pressure chamber within an angular range of 435° to 650° of rotation of the rotating volumetric auger.

[0026] The range of rotation angles for fluid communication between the first through-hole and the back pressure chamber is advantageous because fluid communication between the compression chamber and the back pressure chamber can be achieved within the largest possible range of rotation angles of the rotating volumetric screw. Furthermore, after a large rotation angle, the compression and therefore pressure of the working medium are high, thus allowing a sufficiently high pressure to be applied to the back pressure chamber.

[0027] In a preferred embodiment, the temporary overlap between the first through-hole and the outlet is between 1% and 100%, particularly between 10% and 90%, particularly between 20% and 80%, particularly between 30% and 70%, and particularly between 40% and 60%.

[0028] By maximizing the overlap (überschneiden), the first through-hole is positioned in the high-pressure region of the positive displacement machine for the longest possible time. This achieves an advantageously long period during which the first through-hole is open. The overlap period between the first through-hole and the outlet can be adjusted by varying the degree of overlap.

[0029] In a further preferred embodiment, at least a first compression chamber and a second compression chamber for receiving the working medium are temporarily formed during operation, and a second through hole is arranged in a volumetric auger such that, during operation, by means of the circumferential movement of the volumetric auger, the second through hole is at least partially temporarily arranged in the first compression chamber, and subsequently at least partially temporarily arranged in the second compression chamber.

[0030] Thus, the back pressure chamber is additionally and temporarily in fluid communication with the first and second compression chambers alternately through a second through-hole. This allows the back pressure chamber to be in fluid communication with at least one of the compression chambers and / or the high-pressure area in the outlet region.

[0031] Particularly preferably, the second through hole is arranged in the first compression chamber within an angle range of 95° to 250° of the rotation angle of the rotating volumetric screw, and in the second compression chamber within an angle range of 285° to 650°.

[0032] It is advantageous for the second through-hole to be temporarily positioned within the rotation angle range of the first and second compression chambers, because the second through-hole is in fluid communication with the back pressure chamber for as long as possible.

[0033] Furthermore, compression in the compression chamber occurs as the rotation angle increases. Therefore, the counter-pressure chamber can be subjected to a greater pressure than at smaller rotation angles. In other words, the through-hole is arranged in the first or second compression chamber only from a rotation angle, at which the pressure in the compression chamber is high enough to generate sufficient pressure in the counter-pressure chamber to press the volumetric auger against the counter-auger in a fluid-sealed manner with minimal performance loss.

[0034] Preferably, the first and / or second through holes are arranged in a section at the bottom of the volumetric spiral member. This is advantageous because it makes it easier for the counter-spiral member to pass through the through holes. Furthermore, this allows for a straight and as short a connection as possible to the counter-pressure chamber.

[0035] Advantageously, the first through hole has a smaller diameter than the second through hole, wherein the diameter value is between 0.1 mm and 1 mm.

[0036] Particularly advantageously, the diameter of the first through hole is 0.3 mm and / or the diameter of the second through hole is 0.5 mm.

[0037] Due to their different diameters, the first and second through holes can be adapted to the pressure in the compression chamber. In the radially inner region of the interlocking screws, the degree of compression, and therefore the pressure of the working medium, is higher than in the radially outer region of the interlocking screws. The first through hole is arranged in the radially inner region of the high-compression, volumetric screw. The second through hole is preferably arranged in the radially outer region where the degree of compression is lower than that of the radially inner region. The smaller diameter of the first through hole prevents fluid from flowing from the high-compression or high-pressure region into the counter-pressure chamber. The lower pressure in the radially outer region makes a larger diameter of the second through hole advantageous, so as to apply sufficient pressure to the counter-pressure chamber to press the volumetric screw against the counter-screw.

[0038] In an advantageous embodiment, the first through hole and / or the second through hole has a circular, elliptical, or egg-shaped cross-section.

[0039] This enables various advantageous implementations of the through-hole, which affect the flow characteristics of the working medium. For example, the area of ​​the first through-hole exposed when the anti-rotor passes during operation has a larger cross-section than the area still covered by the anti-rotor. Thus, sufficient fluid communication with the back pressure chamber can be formed before the through-hole is fully opened.

[0040] In a preferred embodiment, the volumetric spiral and / or anti-spiral member has at least a partial chamfer (Fase).

[0041] The chamfer reduces the range of rotation angles required to cover the first and / or second through holes for the anti-spiral component to pass through. Therefore, the chamfer shortens the time required to close the through holes.

[0042] Within the scope of this invention, a method for operating a volumetric machine is disclosed and claimed, wherein, during the operation of the volumetric machine, a first through-hole temporarily overlaps at least partially with an outlet centrally arranged in a counter-rotating member and forms fluid communication with a counter-pressure chamber.

[0043] Furthermore, within the scope of this invention, vehicle air conditioning systems and vehicles having vehicle air conditioning systems are also disclosed and claimed. Attached Figure Description

[0044] The present invention will now be described in more detail with reference to the embodiments and the accompanying drawings.

[0045] In the attached diagram: Figure 1 A cross-section of a volumetric machine according to an embodiment of the present invention is shown; Figure 2 It shows according to Figure 1 Another cross-section of a volumetric machine; Figure 3 A schematic cross-section of a reverse screw and a volumetric screw of a volumetric machine according to an embodiment of the present invention is shown; Figure 4 A schematic cross-section of a reverse screw and a volumetric screw of a volumetric machine according to an embodiment of the present invention is shown during a compression cycle with a rotation angle of 0°. Figure 5 It shows according to Figure 4 A schematic cross-section of a volumetric machine at a rotation angle of 120°; Figure 6 It shows according to Figure 4 A schematic cross-section of a volumetric machine with a rotation angle of 260°; Figure 7 It shows according to Figure 4 A schematic cross-section of a volumetric machine with a rotation angle of 360°; Figure 8 It shows according to Figure 4 A schematic cross-section of a volumetric machine with a rotation angle of 460°; Figure 9 It shows according to Figure 4 A schematic cross-section of a volumetric machine at a rotation angle of 500°; Figure 10 It shows according to Figure 4 A schematic cross-section of a volumetric machine at a rotation angle of 600°; Figure 11 It shows according to Figure 4 A schematic cross-section of a volumetric machine at a rotation angle of 720°. Detailed Implementation

[0046] Figure 1 and Figure 2 Cross-sections of a volumetric machine 10 according to an embodiment of the present invention are shown, such as those used in a vehicle air conditioning system.

[0047] The positive displacement machine 10 includes a housing 19. The housing 19 has a cylindrical shape. A drive 20 is arranged in the housing 19. For example, an electric motor or mechanical drive can be used as the drive 20. The drive 20 is connected to a shaft 21.

[0048] Shaft 21 extends along the longitudinal direction of housing 19. An eccentric bearing 22 with an eccentric pin 23 is arranged at the axial end of shaft 21. A volumetric screw 13 is connected to shaft 21 via the eccentric bearing 22.

[0049] The anti-rotating screw 14 is arranged in the housing 19 on the side of the volumetric screw 13 opposite to the eccentric bearing 22. The anti-rotating screw 14 is fixed and immovably arranged in the housing 19 of the volumetric machine 10. The anti-rotating screw 14 and the housing 19 can be designed as an integral part.

[0050] The high-pressure chamber 11 is arranged on the side of the anti-spiral member 14 opposite to the volumetric spiral member 13.

[0051] The outlet 16 is centrally located within the anti-spiral member 14. The outlet 16 extends between the high-pressure chamber and the side of the anti-spiral member 14 facing the volumetric spiral member 13.

[0052] The low-pressure chamber 12 is arranged on the side of the volumetric spiral member 13 opposite to the anti-spiral member 14. The anti-pressure chamber 15 is arranged between the low-pressure chamber 12 and the volumetric spiral member 13.

[0053] The volumetric screw 13 is movably arranged within the housing 19 in a direction parallel to the longitudinal direction of the shaft 21. In other words, the volumetric screw 13 can move both in the direction of the anti-screw 14 and in a direction away from the anti-screw 14. Figure 2 As can be seen, the first through hole and the second through holes 17a and 17b are arranged in the bottom of the volumetric spiral member 13.

[0054] A first through hole 17a is arranged in the radially inner region of the volumetric auger 13. A second through hole 17b is arranged in the radially outer region of the volumetric auger 13. The first and second through holes 17a and 17b extend perpendicular to the bottom surface. In the installed state, the through holes 17a and 17b extend between the side of the bottom facing the anti-auger 14 and the side of the bottom away from the anti-auger 14.

[0055] Through holes 17a and 17b each have an opening on both sides of the bottom, allowing the two sides of the bottom to communicate with each other. In other words, through holes 17 form a channel between the two sides of the bottom of the volumetric spiral member 13. Through holes 17a and 17b are in fluid communication with the back pressure chamber 15.

[0056] Through holes 17a and 17b have a circular cross-section. Other shapes (e.g., elliptical, egg-shaped, or polygonal) are also possible. Preferably, through holes 17a and 17b have drilled holes. Preferably, the diameters of through holes 17a and 17b are between 0.1 mm and 1 mm. In particular, the diameter of the first through hole 17a is 0.3 mm, and the diameter of the second through hole 17b is 0.5 mm.

[0057] Figure 3 It shows that it can be used according to Figure 1 and Figure 2 A schematic diagram of the volumetric screw 13 and the anti-screw 14 in the volumetric machine 10.

[0058] The volumetric spiral member 13 and the anti-spiral member 14 each have a spiral portion 24 and a bottom. The spiral portion 24 is arranged vertically on the bottom of the volumetric spiral member 13 and the anti-spiral member 14, respectively. The spiral portion 24 has a helical or spiral geometry. In the installed state, the spiral portion 24 of the volumetric spiral member 13 extends in the direction of the anti-spiral member 14, while the spiral portion 24 of the anti-spiral member 14 extends in the direction of the volumetric spiral member 13. The spiral portions 24 of the volumetric spiral member 13 and the anti-spiral member 14 engage with each other. In operation, the spiral portions 24 contact the bottoms of the opposing spiral members 13 and 14, respectively.

[0059] Compression chambers 18a and 18b are formed by interlocking helical members 13 and 14. In other words, compression chambers 18a and 18b are defined by the helical portion 24 of the volumetric helical member 13 and the anti-helical member 14.

[0060] The outlet 16 is centrally and eccentrically arranged in the anti-spiral component 14. In addition to the outlet 16, two secondary outlets 25a and 25b are arranged in the anti-spiral component 14. The secondary outlets 25a and 25b can also be referred to as pre-outlets. The secondary outlets 25a and 25b are radially spaced from the center of the anti-spiral component 14.

[0061] The internal compression chamber 26 is arranged in the radially internal region of the two interlocking spiral members 13, 14. The description of the discharge outlet as "centrally or centrally arranged" means that the discharge outlet at least partially and temporarily coincides with the internal compression chamber 26 defined by the volumetric spiral member 13 and the anti-spiral member 14.

[0062] exist Figures 4 to 11 The image schematically illustrates various states of the compression cycle of the volumetric machine 10. In the following description, the relative positions of the volumetric auger 13 and the anti-auger 14 are depicted in a momentary photograph to understand the geometry of each component and its function or effect. Figures 4 to 11 The spiral arrangement shown is structurally essentially corresponding to Figure 3 The spiral arrangement shown.

[0063] A compression cycle can be understood as the continuous and repeated operation or period of a compression process.

[0064] The position of the volumetric screw 13 during the compression cycle can be represented by the rotation angle of the circumferential motion. Figure 4 The rotation angle of the volumetric spiral component 13 is 0°.

[0065] exist Figure 4 In this structure, a first compression chamber and second compression chambers 18a and 18b are formed in the radially outer region. Both compression chambers 18a and 18b are closed.

[0066] When the compression chamber 18 is surrounded by the helical portion 24 of the volumetric helical member 13 and the anti-helical member 14 in a fluid-tight manner, the compression chamber 18 is closed.

[0067] The other first and second compression chambers 18c and 18d are respectively arranged in the radial inner regions of the screws 13 and 14. Compression chambers 18c and 18d have relatively smaller volumes than compression chambers 18a and 18b.

[0068] The relative volume of the compression chamber 18 is understood as the change in volume of the compression chamber 18 relative to its initial volume when the rotation angle is 0° at a given point in time during the compression cycle of the positive displacement machine 10.

[0069] The first through-hole 17a is covered by the spiral portion 24 of the anti-spiral member 14. The second through-hole 17b is arranged in the second compression chamber 18d. Therefore, the first through-hole 17a is closed and the second through-hole 17b is open. As a result, there is fluid communication between the second compression chamber 18d and the counter-pressure chamber 15, and the volumetric spiral member 13 is pressed against the anti-spiral member 14.

[0070] Figure 5 The image shows an instantaneous shot taken at a rotation angle of 120°. Compression chambers 18a and 18b have migrated radially inward. The relative volume of compression chambers 18a and 18b has decreased.

[0071] The relative volume of compression chambers 18a and 18b decreases as the rotation angle increases. By decreasing the relative volume, the pressure in compression chambers 18a and 18b increases.

[0072] Compression chambers 18c and 18d are combined to form an internal compression chamber 26. Preferably, the internal compression chamber 26 corresponds to the high-pressure region where the first through-hole 17a is arranged.

[0073] The first through-hole 17a is arranged in the internal compression chamber 26 or the high-pressure area. The first through-hole 17a coincides with the outlet 16. The second through-hole 17b is arranged in the first compression chamber 18a. Therefore, both through-holes 17a and 17b are open and can achieve fluid communication with the back pressure chamber 15.

[0074] The term "overlapping" is understood to mean that two openings 17a, 16 are at least partially arranged on top of the other. The first through-hole 17a is a distance away from the outlet 16 in the direction of the anti-spiral member 14. In other words, the through-hole 17a at least partially covers, sweeps through, and / or traverses the outlet 16.

[0075] The partial overlap of the first through-hole 17a allows for the setting of the highest possible pressure in the back pressure chamber 15. Furthermore, this enables the back pressure chamber 15 to maintain fluid communication with the high-pressure region for the longest possible time period or over a wide range of rotation angles.

[0076] Figure 6 A view of a compression cycle with a rotation angle of 260° is shown.

[0077] The first and second compression chambers 18a and 18b migrate further radially inward. The relative volume of the inner compression chamber 26 with the first and second compression chambers 18a and 18b has decreased. Therefore, the pressure in the compression chambers 18a and 18b further increases.

[0078] The first through-hole 17a is also arranged in the internal compression chamber 26. The first through-hole 17a no longer overlaps with the discharge port 16. The second through-hole 17b is covered by the spiral portion 24 of the anti-spiral component 14. Figure 6 In the middle, the pressure in the back pressure chamber 15 is generated through the fluid communication between the first through hole 17a and the internal compression chamber.

[0079] Figure 7 The image shows a momentary shot of a compression cycle with a rotation angle of 360°.

[0080] Two new compression chambers 18e and 18f are formed in the radial outer regions of the volumetric spiral member 13 and the anti-spiral member 14.

[0081] The first and second compression chambers 18a and 18b further migrate in the direction of the center and the outlet 16. The relative volume of the inner compression chamber 26 is further reduced. The outlet 16 is partially arranged in 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 outlet 16.

[0082] The first through-hole 17a is covered by the spiral portion 24 of the anti-spiral member 14 and is therefore closed. The second through-hole 17b is arranged in the second compression chamber 18b after passing through the spiral portion 24 and is open.

[0083] Figure 8 The compression process is shown when the rotation angle is 460°.

[0084] Compression chambers 18e and 18f further migrate in the direction of discharge port 16. The relative volume of compression chambers 18e and 18f further decreases.

[0085] The internal compression chamber 26 formed by merging the first compression chamber and the second compression chambers 18c and 18d disappears. The first compression chamber and the second compression chambers 18a and 18b are merged into a new internal compression chamber 26.

[0086] A first through-hole 17a is arranged in the inner compression chamber 26. The first through-hole 17a overlaps with the outlet 16. A second through-hole 17b is partially covered by the spiral portion 24 of the anti-spiral member 14 extending between the first compression chamber 18c and the inner compression chamber 26. The second through-hole 17b is partially open.

[0087] The first through-hole 17a is in fluid communication with the high-pressure area or the internal compression chamber 26 and the back pressure chamber 15. This has a favorable effect on the pressure in the back pressure chamber 15 because the second through-hole 17b is not fully open, but only partially open, thus setting a low pressure at that point in the compression cycle in the absence of the first through-hole 17a.

[0088] Figure 9 The image shows a moment captured during a compression cycle at 500°.

[0089] The relative volumes of compression chambers 18e, 18f and internal compression chamber 26 are further reduced.

[0090] The outlet 16 is fully disposed within the internal compression chamber 26. The first through-hole 17a is also disposed within the internal compression chamber 26 and overlaps with the outlet 16. The second through-hole 17b is disposed entirely within the first compression chamber 18e, no longer partially disposed. Both through-holes 17a and 17b are open and in fluid communication with the back pressure chamber 15.

[0091] At a rotation angle of 600° Figure 10 In the middle, the outlet 16 is still arranged in the internal compression chamber 26. The first through hole 17a does not overlap with the outlet 16.

[0092] The second through hole 17b is arranged in the first compression chamber 18e. The second through hole 17b abuts tangentially against the spiral portion 24.

[0093] Figure 11 This shows a state that essentially corresponds to a rotation angle of 360° (see...) Figure 7 The state of the compression loop, where with Figure 7 The state shown is the opposite. Figure 11The internal compression chamber 26 is formed by compression chambers 18a and 18b.

[0094] Shaft 21 is operatively connected to driver 20. In operation, rotation of shaft 21 and eccentric connection of volumetric screw 13 to shaft 21 cause circumferential motion of volumetric screw 13.

[0095] At the start of the compression cycle, the working medium (e.g., coolant) is drawn from the low-pressure chamber 12 into the radially outer region of the screws 13 and 14. The working medium is transported in the compression chamber 18 between the volumetric screw 13 and the anti-screw 14. The circumferential motion of the volumetric screw 13 reduces the relative volume of the compression chamber 18 to compress the working medium.

[0096] As the compression cycle proceeds, compression chamber 18 disappears. In other words, compression chamber 18 is temporary. During operation, compression chamber 18 is formed successively in the radially outer region of the helical arrangement, and then migrates to the radially inner region of the helical arrangement. The movement path of compression chamber 18 is helical. In the radial interior of the helical members 13 and 14, the first and second compression chambers 18a and 18b initially merge to form an inner compression chamber 26. The relative volume of the inner compression chamber 26 further decreases until the inner compression chamber 26 disappears. Immediately afterwards, two successive first and second compression chambers 18c and 18d form a new inner compression chamber 26.

[0097] The compressed working medium flows from the internal compression chamber 26 into the high-pressure chamber 11 through the discharge port 16.

[0098] exist Figures 4 to 11 In the embodiment shown, there can be up to five compression chambers 18, 26. Here, there are two pairs of first and second compression chambers 18a, 18b and one internal compression chamber 26. Configurations containing more or fewer compression chambers 18, 26 are also possible.

[0099] Through holes 17a and 17b move due to the circumferential motion of the volumetric auger 13 along a circular path. Through holes 17a and 17b allow the compression chambers 18 and 26 to be fluidly connected to the counter-pressure chamber 15 during operation, so as to apply sufficient pressure to the volumetric auger 13, thereby pressing the volumetric auger 13 against the counter-auger 14.

[0100] In the compression cycle, the through holes 17a and 17b are preferably open within the following angular ranges: Within a rotation angle range of 435° to 650°, the first through hole 17a forms fluid communication between the internal compression chamber 26 and the counter-pressure chamber 15. Within a rotation angle range of 95° to 250°, the second through hole 17b forms fluid communication with the first compression chamber 18a and the counter-pressure chamber 15. Within an angular range of 285° to 650°, the second through hole 17b is arranged in the second compression chamber 18b. Within a rotation angle range of 250° to 285°, the second through hole 17b is covered by the helical portion 24 of the anti-spiral member 14. When the second through hole 17b is covered by the anti-spiral member, it is preferred, but not mandatory, for the first through hole 17a to be open, and vice versa. Figure 6 In the instantaneous image taken at a rotation angle of 260°, the second through-hole 17b is closed. The previous compression cycle has not yet been completed. The position of the rotation angle of the previous compression cycle corresponds to... Figure 6 Approximately 620°. Therefore, the first through-hole 17a is arranged in the internal compression chamber 26, thereby enabling fluid communication with the counter-pressure chamber 15.

[0101] During operation of the positive displacement machine 10, the second through-hole 17b is first arranged in the first compression chamber 18a, and then arranged in the second compression chamber 18b of the compression cycle. The second through-hole 17b is arranged once in one of the compression chambers 18a and 18b in each compression cycle. After the second compression chamber 18b, the second through-hole 17b migrates to the first compression chamber 18c of the subsequent compression cycle.

[0102] Part of the working medium flows into the counter-pressure chamber 15 through through holes 17a and 17b. This increases the pressure in the counter-pressure chamber 15. Due to this pressure, the volumetric auger 13 is subjected to an axial force. This force acts in the direction of the counter-auger 14. Since the volumetric auger 13 can move in the axial direction, it is pressed against the counter-auger 14. The pressing of the volumetric auger 13 against the counter-auger 14 results in the compression of the working medium with the lowest possible performance loss.

[0103] exist Figures 4 to 11 In the exemplary embodiment shown, multiple compression cycles occur simultaneously with a time delay. First compression chambers and second compression chambers 18a, 18b, as well as first compression chambers and second compression chambers 18c, 18d, are associated with different compression cycles. In other words, each compression cycle includes a pair of first compression chambers and second compression chambers 18a, 18b.

[0104] Reference tag list

Claims

1. A volumetric machine based on a helical principle, comprising a high-pressure chamber (11), a low-pressure chamber (12), a rotating volumetric helical element (13), a reverse helical element (14), and a counter-pressure chamber (15) between the low-pressure chamber (12) and the rotating volumetric helical element (13), wherein an outlet (16) in the reverse helical element (14) is centrally located in the high-pressure region, and a working medium compressed during operation flows into the high-pressure chamber (11) through the outlet, and wherein the rotating volumetric helical element (13) has at least a first through-hole (17a) and a second through-hole (17b) for fluid communication with the counter-pressure chamber (15). in, At least the first through hole (17a) is arranged in the region of the outlet (16) such that during operation the first through hole (17a) and the outlet (16) at least partially and temporarily overlap, wherein the first through hole (17a) is in fluid-conducting communication with the back pressure chamber (15) in an angle range of 435° to 650° of the rotation angle of the rotating volumetric auger (13).

2. The volumetric machine according to claim 1, Its features are, The second through hole (17b) is arranged in the region of the rotating volumetric screw (13) which has a lower pressure than that in the high-pressure region during operation.

3. The volumetric machine according to claim 1, Its features are, The temporary overlap between the first through hole (17a) and the outlet (16) is between 1% and 100%.

4. The volumetric machine according to claim 2, Its features are, The temporary overlap between the first through hole (17a) and the outlet (16) is between 1% and 100%.

5. The volumetric machine according to claim 3 or 4, Its features are, The temporary overlap between the first through hole (17a) and the outlet (16) is between 10% and 90%.

6. The volumetric machine according to claim 5, Its features are, The temporary overlap between the first through hole (17a) and the outlet (16) is between 20% and 80%.

7. The volumetric machine according to claim 6, Its features are, The temporary overlap between the first through hole (17a) and the outlet (16) is between 30% and 70%.

8. The volumetric machine according to claim 7, Its features are, The temporary overlap between the first through hole (17a) and the outlet (16) is between 40% and 60%.

9. The volumetric machine according to any one of claims 1-4 and 6-8, Its features are, In operation, at least a first compression chamber (18a) and a second compression chamber (18b) for receiving the working medium are temporarily formed, and a second through hole (17b) is arranged in the swirling volumetric auger (13) such that, in operation, by the swirling movement of the swirling volumetric auger (13), the second through hole (17b) is at least partially temporarily arranged in the first compression chamber (18a), and subsequently at least partially temporarily arranged in the second compression chamber (18b).

10. The volumetric machine according to claim 5, Its features are, In operation, at least a first compression chamber (18a) and a second compression chamber (18b) for receiving the working medium are temporarily formed, and a second through hole (17b) is arranged in the swirling volumetric auger (13) such that, in operation, by the swirling movement of the swirling volumetric auger (13), the second through hole (17b) is at least partially temporarily arranged in the first compression chamber (18a), and subsequently at least partially temporarily arranged in the second compression chamber (18b).

11. The volumetric machine according to claim 9, Its features are, The second through hole (17b) is arranged in the first compression chamber (18a) with a rotation angle of 95° to 250° of the rotating volumetric screw (13), and in the second compression chamber (18b) with a rotation angle of 285° to 650°.

12. The volumetric machine according to claim 10, Its features are, The second through hole (17b) is arranged in the first compression chamber (18a) with a rotation angle of 95° to 250° of the rotating volumetric screw (13), and in the second compression chamber (18b) with a rotation angle of 285° to 650°.

13. The volumetric machine according to any one of claims 1-4, 6-8, and 10-12, Its features are, The first through hole (17a) and / or the second through hole (17b) are arranged in the section at the bottom of the rotating volumetric spiral (13).

14. The volumetric machine according to claim 5, Its features are, The first through hole (17a) and / or the second through hole (17b) are arranged in the section at the bottom of the rotating volumetric spiral (13).

15. The volumetric machine according to claim 9, Its features are, The first through hole (17a) and / or the second through hole (17b) are arranged in the section at the bottom of the rotating volumetric spiral (13).

16. The volumetric machine according to any one of claims 1-4, 6-8, 10-12, and 14-15, Its features are, The first through hole (17a) and / or the second through hole (17b) have a circular, elliptical or egg-shaped cross-section.

17. The volumetric machine according to claim 5, Its features are, The first through hole (17a) and / or the second through hole (17b) have a circular, elliptical or egg-shaped cross-section.

18. The volumetric machine according to claim 9, Its features are, The first through hole (17a) and / or the second through hole (17b) have a circular, elliptical or egg-shaped cross-section.

19. The volumetric machine according to claim 13, Its features are, The first through hole (17a) and / or the second through hole (17b) have a circular, elliptical or egg-shaped cross-section.

20. The volumetric machine according to any one of claims 1-4, 6-8, 10-12, 14-15, and 17-19, Its features are, The diameter of the first through hole (17a) is smaller than the diameter of the second through hole (17b), wherein the diameter value is between 0.1 mm and 1 mm.

21. The volumetric machine according to claim 5, Its features are, The diameter of the first through hole (17a) is smaller than the diameter of the second through hole (17b), wherein the diameter value is between 0.1 mm and 1 mm.

22. The volumetric machine according to claim 9, Its features are, The diameter of the first through hole (17a) is smaller than the diameter of the second through hole (17b), wherein the diameter value is between 0.1 mm and 1 mm.

23. The volumetric machine according to claim 13, Its features are, The diameter of the first through hole (17a) is smaller than the diameter of the second through hole (17b), wherein the diameter value is between 0.1 mm and 1 mm.

24. The volumetric machine according to claim 16, Its features are, The diameter of the first through hole (17a) is smaller than the diameter of the second through hole (17b), wherein the diameter value is between 0.1 mm and 1 mm.

25. The volumetric machine according to any one of claims 1-4, 6-8, 10-12, 14-15, 17-19 and 21-24, Its features are, The first through hole (17a) has a diameter of 0.3 mm and / or the second through hole (17b) has a diameter of 0.5 mm.

26. The volumetric machine according to claim 5, Its features are, The first through hole (17a) has a diameter of 0.3 mm and / or the second through hole (17b) has a diameter of 0.5 mm.

27. The volumetric machine according to claim 9, Its features are, The first through hole (17a) has a diameter of 0.3 mm and / or the second through hole (17b) has a diameter of 0.5 mm.

28. The volumetric machine according to claim 13, Its features are, The first through hole (17a) has a diameter of 0.3 mm and / or the second through hole (17b) has a diameter of 0.5 mm.

29. The volumetric machine according to claim 16, Its features are, The first through hole (17a) has a diameter of 0.3 mm and / or the second through hole (17b) has a diameter of 0.5 mm.

30. The volumetric machine according to claim 20, Its features are, The first through hole (17a) has a diameter of 0.3 mm and / or the second through hole (17b) has a diameter of 0.5 mm.

31. The volumetric machine according to any one of claims 1-4, 6-8, 10-12, 14-15, 17-19, 21-24, and 26-30, Its features are, The swirling volumetric spiral (13) and / or the anti-spiral (14) have at least a partial chamfer.

32. The volumetric machine according to claim 5, Its features are, The swirling volumetric spiral (13) and / or the anti-spiral (14) have at least a partial chamfer.

33. The volumetric machine according to claim 9, Its features are, The swirling volumetric spiral (13) and / or the anti-spiral (14) have at least a partial chamfer.

34. The volumetric machine according to claim 13, Its features are, The swirling volumetric spiral (13) and / or the anti-spiral (14) have at least a partial chamfer.

35. The volumetric machine according to claim 16, Its features are, The swirling volumetric spiral (13) and / or the anti-spiral (14) have at least a partial chamfer.

36. The volumetric machine according to claim 20, Its features are, The swirling volumetric spiral (13) and / or the anti-spiral (14) have at least a partial chamfer.

37. The volumetric machine according to claim 25, Its features are, The swirling volumetric spiral (13) and / or the anti-spiral (14) have at least a partial chamfer.

38. The volumetric machine according to any one of claims 1-4, 6-8, 10-12, 14-15, 17-19, 21-24, 26-30 and 32-37, Its features are, The positive displacement machine is a scroll compressor.

39. The volumetric machine according to claim 5, Its features are, The positive displacement machine is a scroll compressor.

40. The volumetric machine according to claim 9, Its features are, The positive displacement machine is a scroll compressor.

41. The volumetric machine according to claim 13, Its features are, The positive displacement machine is a scroll compressor.

42. The volumetric machine according to claim 16, Its features are, The positive displacement machine is a scroll compressor.

43. The volumetric machine according to claim 20, Its features are, The positive displacement machine is a scroll compressor.

44. The volumetric machine according to claim 25, Its features are, The positive displacement machine is a scroll compressor.

45. The volumetric machine according to claim 31, Its features are, The positive displacement machine is a scroll compressor.

46. ​​A method for operating a volumetric machine based on a helical principle, the volumetric machine having a high-pressure chamber (11), a low-pressure chamber (12), a rotating volumetric helical member (13), a reverse helical member (14), and a counter-pressure chamber (15) between the low-pressure chamber (12) and the rotating volumetric helical member (13), wherein an outlet (16) in the reverse helical member (14) is centrally arranged in the high-pressure region, wherein the rotating volumetric helical member (13) has at least a first through-hole (17a) and a second through-hole (17b) for fluid communication with the counter-pressure chamber (15), and the first through-hole (17a) is arranged in the region of the outlet (16), wherein, During operation of the volumetric machine (10), the compressed working medium flows into the high-pressure chamber (11), and the first through-hole (17a) at least partially and temporarily overlaps with the outlet (16) centrally arranged in the anti-spiral member (14) and forms fluid communication with the counter-pressure chamber (15). The first through hole (17a) is connected to the back pressure chamber (15) in a fluid-conducting manner within the rotation angle range of 435° to 650° of the rotating volumetric spiral (13).

47. The method according to claim 46, Its features are, The positive displacement machine is a scroll compressor.

48. A vehicle air conditioning system comprising a volumetric machine according to any one of claims 1 to 45.

49. A means of transport having a volumetric machine according to any one of claims 1 to 45 or a means of transport air conditioning system according to claim 48.

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