Apparatus for compressing gas fluid and method for operating apparatus for compressing gas fluid

Abstract

An apparatus for compressing a gaseous fluid, particularly a refrigerant compressor for an automotive air conditioning system, and a method for operating a corresponding apparatus for compressing a gaseous fluid are provided. [Solution] The devices for compressing gaseous fluids each have a housing defining a cylindrical cavity within which a helical nozzle assembly is disposed. The helical nozzle assembly thus comprises a helically rotating winding having a winding surface that at least partially sealably contacts the inner wall of the cylindrical cavity. Recesses defining a filter function and a bypass function are disposed on the winding surface of the helically rotating winding, or alternatively, the winding surface of the helically rotating winding is disposed so as to be spaced apart from the inner wall of the cylindrical cavity in at least one partial region by a distance that defines a gap between the filter function and the bypass function. Additionally or alternatively, the recesses defining the filter function are disposed on the collar surface of a collar connected to the helical nozzle assembly.

Description

[Technical Field]

[0001] The present invention relates to a device for compressing a gaseous fluid and a method of operating the device, particularly to a scroll compressor for an automotive air conditioning system, more particularly a refrigerant compressor, in which a helical nozzle assembly is disposed within a cylindrical cavity incorporated in a housing. The helical nozzle assembly has a helically rotating winding having a plurality of turns and a winding surface. The winding surface of the winding is disposed at least partially in sealing contact with the inner wall of the cylindrical cavity. The present invention also relates to a method of operating an apparatus for compressing a gaseous fluid, particularly a scroll compressor for an automotive air conditioning system, and more particularly a refrigerant compressor. [Background technology]

[0002] Prior art compressors for conveying refrigerant through a refrigerant circuit (also called refrigerant compressors) for mobile applications, particularly automotive air conditioning systems, are often configured as variable displacement piston or scroll compressors, regardless of the refrigerant, and are therefore driven via a pulley or electrically. In addition to the housing, a conventional scroll compressor includes a stationary stator having a disk-shaped base plate and a spiral wall extending from one side of the base plate, and a movable orbiter having a disk-shaped base plate and a spiral wall extending from the front side of the base plate. The stator and orbiter cooperate with each other. The base plates are thus positioned relative to each other so that the spiral walls engage with each other. The orbiter moves in a circular orbit by an eccentric drive.

[0003] Prior art scroll compressors also have a wall, also called a counter wall, arranged in a housing and rigidly connected to the housing, that defines a counter pressure region. Due to the counter pressure present in the counter pressure region defined between the counter wall and the orbiter, particularly between the counter wall and the back surface of the orbiter's base plate, the orbiter is pressed against the stator, which is fixed to the housing, with an axial force. The axial force is controlled or adjusted by the counter pressure present in the counter pressure region, also called a contact pressure. Thus, the contact pressure, referred to as the intermediate or intermediate pressure, is between the high pressure, which corresponds to the compressor's outlet pressure, and the low pressure, which corresponds to the compressor's suction pressure.

[0004] The high pressure and counter pressure, and counter pressure and low pressure regions are connected to one another via passages arranged, for example, within the housing or within a drive shaft with an integral expansion device. Counter pressure is generated by the refrigerant mass flow, which is regulated by the expansion device, specifically the combination of a control valve (also called a counter pressure valve) and a spiral nozzle. As a result, particles present in the refrigerant may accumulate in the spiral nozzle flow passage, resulting in blockage of the spiral nozzle flow passage. Such blockage may lead to compressor malfunctions, e.g., pressure regulation errors, and reduce the operating efficiency of the refrigerant compressor.

[0005] To avoid blockage of the flow duct of the spiral nozzle and the associated problems, filters have traditionally been employed, particularly in electrically driven refrigerant compressors for automotive air conditioning systems, which are positioned upstream of the spiral nozzle in the refrigerant flow direction to filter particles from the refrigerant mass flow that could cause blockage of the flow duct. Patent Document 1 discloses a scroll compressor with an oil return unit, particularly for use in automotive air conditioning systems. The compressor draws gaseous refrigerant through a suction pressure chamber between a fixed stator and a moving orbiter and compresses it into a high-pressure chamber. A counter-pressure chamber, also bounded by the orbiter, is also formed. The counter-pressure chamber presses the orbiter against the fixed stator, creating a force balance that minimizes friction and allows the orbiter to move in an orbital spiral within the fixed spiral.

[0006] A suction pressure helical nozzle is disposed within the compressor housing, particularly the central housing, having a cylindrical cavity preferably configured as a cylinder bore, with a helical nozzle assembly disposed therein. The helical nozzle assembly interacts with the wall of the cylindrical cavity such that a helical nozzle is formed between the surface of the helical nozzle assembly and the wall of the cylindrical cavity. Thus, the surface of the helical nozzle assembly has helical grooves, also called windings, that form a helical flow duct or throttle duct at the contact area between the helical nozzle assembly and the wall of the cylindrical cavity. Refrigerant compressors configured as scroll compressors with such helical nozzle assemblies conventionally have a filter in the refrigerant flow direction upstream of the helical nozzle to prevent blockage of the flow duct of the helical nozzle. For this purpose, it is known to employ a filter with a mesh size of, for example, 125 μm.

[0007] The use of such an additional filter requires corresponding additional installation space, at least one corresponding assembly step for arranging the filter, and therefore additional costs in the manufacture of the compressor. In practice, it has been found that due to the impossibility of achieving complete cleaning of the manufacturing and assembly processes during the production of refrigerant compressors, impurities or particles, such as chips, can reach the areas traversed by the refrigerant, which can cause blockages in the inlet area of ​​the helical nozzle and thus in the area of ​​the start of the helical turns of the helical nozzle assembly. As a result, there is a need for improved refrigerant compressors for air conditioning systems and improved methods of operating refrigerant compressors. [Prior art documents] [Patent documents]

[0008] [Patent Document 1] German Patent Application Publication No. 102019101955 Summary of the Invention [Problem to be solved by the invention]

[0009] It is an object of the present invention to provide an apparatus for compressing a gaseous fluid, in particular a refrigerant compressor for an air conditioning system of a motor vehicle, and a method of operating a corresponding apparatus for compressing a gaseous fluid, whereby reliable functioning or safe operation is achieved, such that the labor involved in manufacturing and operating the apparatus, the associated costs, the required installation space, and the number of parts should be minimized. [Means for solving the problem]

[0010] The invention is achieved by the subject matter characterized in the independent claims. Developments are defined in the dependent claims. The invention is achieved by an apparatus according to the invention for compressing a gaseous fluid, in particular a scroll compressor for compressing a refrigerant circulating in a refrigerant circuit, more particularly a refrigerant compressor, which comprises a housing and a compression mechanism with a fixed stator and a moving orbiter. The helical nozzle assembly is disposed within a cylindrical cavity, particularly a cylindrical cavity, configured within the housing, and includes a helically rotating winding having a plurality of turns and a winding surface, the winding surface of the winding being disposed such that the winding surface at least partially sealingly contacts the inner wall of the cylindrical cavity, preferably along the entire length of the winding.

[0011] In the inlet region, the helical nozzle assembly may also be configured with a collar, particularly a circular-cylindrical collar, that sealably abuts the inner wall of the cylindrical cavity with a radially facing collar surface. The collar is located on the helical nozzle assembly in a region upstream of the helical winding in the direction of fluid flow through the helical nozzle assembly. The inlet region refers to the region where the fluid enters the cylindrical cavity with the helical nozzle assembly and thus into the helical nozzle. The helical winding begins with a first turn at the entrance region of the cylindrical cavity or helical nozzle and has multiple turns configured along the outside of the helical nozzle assembly. Multiple is understood to mean at least two. When the winding disposed in the helical nozzle assembly is helically wound or rotated, with the winding surface at least partially in close contact with the inner wall of the cylindrical cavity, the mass flow of fluid is directed through a flow duct configured between adjacent turns of the winding, which also rotates helically as it flows through the helical nozzle. In this way, the fluid flows from the entrance side of the helical nozzle or helical nozzle assembly to the exit side of the helical nozzle. The exit side of the cylindrical cavity of the helical nozzle is preferably configured in the shape of a nozzle. In the inlet region of the helical nozzle, where the helically wound winding of the helical nozzle assembly begins, means for a bypass function are arranged according to the invention, which make it possible to maintain the mass flow of fluid through the helical nozzle, in particular through the helical flow ducts formed between adjacent turns of the helical winding, in the event of a blockage occurring in the inlet region of the helically wound winding.

[0012] The means for configuring a bypass function simultaneously performs a filter function for filtering impurities from the mass flow of fluid in the inlet region of the helical nozzle. In a first device according to the invention, recesses constituting the filter and bypass functions are arranged on the winding surface of the spirally rotating winding and / or recesses constituting the filter function are arranged on the collar surface of a collar connected to the spiral nozzle assembly. Preferably, the recesses each have the form of a slot, each extending between two adjacent free volumes acted upon by the fluid and connecting the volumes with each other. To perform the bypass function, a plurality of recesses are formed in the winding surface of the winding, particularly in the winding surface of the start end of the helically rotating winding or the first turn of the helically rotating winding, and thus in the inlet region of the helical nozzle. These recesses advantageously communicate with the inner wall of the cylindrical cavity and extend parallel to the central axis or axis of symmetry of the cylindrical cavity or the longitudinal axis of the helical nozzle assembly, respectively, and represent a bypass for fluid passing through the normally sealed region between the winding surface of the winding and the inner wall of the cylindrical cavity, and thus to the helically rotating flow duct. As a bypass function, each recess in the winding surface allows overflow of fluid from the inlet region into a first region of the flow duct, which is also formed between two adjacent turns of the winding or two adjacent sections of the flow duct of the helical nozzle.

[0013] In this way, the bypass function serves to allow the fluid to pass through the spiral nozzle even if impurities, such as chips, are present in the fluid and would lead to blockage of the spiral nozzle at the inlet area or the beginning of the spiral winding, thereby avoiding malfunctions or failures of the device due to such blockages and ensuring operation of the device even in the event of such blockages. Due to their dimensions, the means for bypassing, configured as recesses, perform a filtering function in addition to the bypassing function when a blockage occurs, since particles contained in the fluid that exceed a predetermined size based on the dimensions of the recesses cannot pass through the flow cross-section defined by the recesses in communication with the inner wall, and are therefore filtered out of the mass flow of the fluid, as they are prevented from flowing through the flow cross-section.

[0014] According to the present invention, the recesses formed on the winding surface of the first turn of the winding are arranged over the area of ​​an arc of the first turn, and thus in a cross section of the first turn of the winding. Thus, the recesses can be arranged along the entire circumference of the first turn of the winding. Furthermore, groups with a certain number of recesses can be arranged on different arcs or sections of the first turn of the winding. Thus, the area in which the recesses are arranged can be the entire first turn, or an arc or multiple arcs within the area of ​​the first turn. Alternatively or additionally, the filtering function is enabled by the configuration of a plurality of recesses on the collar surface of the collar connected to the helical nozzle assembly, the recesses preferably extending parallel to the central axis or axis of symmetry of the cylindrical cavity or the longitudinal axis of the helical nozzle assembly. The collar provided at the inlet region of the helical nozzle or helical nozzle assembly is preferably in the form of a circumferential ring, with the circumferential collar surface sealingly fitting against the inner wall of the cylindrical cavity.

[0015] A further advantage of the present invention is that the recesses distributed around the circumference of the circumferential collar surface of the collar are arranged in partial regions, in particular arc regions, around the circumference of the collar, or distributed over the entire circumference of the collar. Alternatively, recesses in multiple arc regions can be distributed around the circumference of the circumferential collar surface, or groups with a certain number of recesses can be arranged in different arcs or parts of the circumference of the circumferential collar surface. The filtering function of such a collar is alternatively ensured over a defined distance between the circumferential collar surface and the inner wall of the cylindrical cavity, the outer diameter of the collar being slightly smaller than the inner diameter of the inner wall of the cylindrical cavity, thereby defining a filtering gap whose size is in the range of 0.01 mm to 0.30 mm.

[0016] In the device of the present invention, the winding surface of the spirally rotating winding is arranged in at least one partial region spaced apart from the inner wall of the cylindrical cavity, forming a gap. Thus, the partial area of ​​the spirally rotating winding surface that is spaced apart from the inner wall of the cylindrical cavity preferably spans an angle between 0° and 360°, and thus spans at least the first turn, or only a portion of the angle between 0° and 360° of the first turn of the winding. Thus, embodiments with an angle between 0° and 720° or more are also conceivable, thereby forming at least two turns of the rotating winding. The gap formed between the winding surface of the spirally rotating winding and the inner wall of the cylindrical cavity can decrease or remain constant in the inlet region of the spiral nozzle as the distance from the beginning of the winding increases. This gap allows both a bypass function in case of blockages in the inlet region of the spiral nozzle assembly and a filter function for retaining particles of a certain size.

[0017] The distance between the winding surface and the inner wall of the cylindrical cavity, particularly in the area of ​​the first turn of the winding, can be in the range of 0.001 mm to 0.250 mm. According to the invention, the gap extends over the entire circumference of the first revolution, with the distance between the winding surface of the spirally rotating winding and the inner wall of the cylindrical cavity remaining constant. Alternatively, the gap distance along the first turn of the winding is configured to be small, so that at the start of the winding in the inlet region of the spiral nozzle, and therefore at the start of the first turn of the winding, the gap is 0 mm between the winding surface of the spirally rotating winding and the inner wall of the cylindrical cavity. In the direction of progression of the first turn, the gap distance decreases to 0 mm, and at the end of the first turn, and therefore at the start of the second turn of the winding, the winding surface is in perfect sealing contact with the inner wall of the cylindrical cavity, for example. Thus, the progression of the reduction in the gap distance may be continuous or ramped, a ramped configuration being understood as a configuration of sections along the winding surface in which the distance within the corresponding section is constant.

[0018] According to a development of the invention, the size of the gap distance is configured to change in a ramp-like manner in the range from 0.20 mm to 0 mm, in particular in the range from 0.08 mm to 0 mm, or the gap distance has a fixed size in the range from 0.01 mm to 0.20 mm, in particular in the range from 0.08 mm to 0.20 mm. Sizing the gap distance ensures that the fluid flows through the gap in a manner that ensures mass flow of the fluid through the helical nozzle, while correspondingly larger impurities in the fluid are retained by the gap. In addition to the spaced arrangement of the winding surfaces of the helically rotating windings of the helical nozzle assembly against the inner wall of the cylindrical cavity, the filtering function can again be performed by configuring a plurality of recesses in the collar surface of the collar connected to the helical nozzle assembly. The recesses, in turn, preferably extend parallel to the central axis or axis of symmetry of the cylindrical cavity or the longitudinal axis of the helical nozzle assembly and can be configured as described above.

[0019] The dimensions of each recess in the collar surface are also selected to prevent particles above a predetermined size from passing between the recess and the inner wall of the cylindrical cavity, thereby being retained or filtered out. According to the invention, the recesses configured in the winding surface or the collar surface each have a semicircular, rectangular, trapezoidal or triangular cross section. The various recesses can be incorporated into the winding surface of the winding and / or the collar surface in various ways. To enable the bypass function, the cross section of the recesses is selected to be large so that the flow cross section defined by the recess in communication with the inner wall of the cylindrical cavity ensures the desired mass flow rate of the fluid. In this way, the flow cross section, and therefore also the cross section of the recess, is selected to be very small so that particles having a predetermined minimum size are retained or filtered, thus fulfilling the filter function.

[0020] Advantageously, the recesses have a width in the range of 0.01 mm to 0.02 mm and a depth in the range of 0.008 mm to 0.01 mm, the dimensions of the recesses being such that the fluid can pass through the recesses while correspondingly retaining larger impurities in the fluid. Depending on their size or dimensioning and arrangement, each recess acts as a filter, not allowing particles contained in the fluid above a certain size level to pass through. The present invention also includes any combination of the described embodiments for implementing the filter and bypass functions. Thus, for example, a collar arrangement with a recess can be combined with a recess arranged in the region of the first turn of the spiral winding. Alternatively, a collar arrangement with a recess can be combined with a gap arranged in the region of the first turn, the gap being either a constant distance or a distance that varies over the length and thus the course of the winding, starting from the inlet region. Each combination further improves the filter function in particular.

[0021] This object is also achieved by a method of operating a device for compressing a gaseous fluid, in particular a scroll compressor for an automotive air conditioning system. In this method, a helical nozzle assembly having a helically rotating winding is provided within a cylindrical cavity incorporated in a housing, the winding surface of the winding being at least partially disposed in sealable contact with an inner wall of the cylindrical cavity, and a mass flow of fluid within the helical nozzle assembly is directed through a helically configured flow duct during rotation of the winding. The winding surface area of ​​the winding is provided with a bypass function and a filter function. Additionally or alternatively, the collar surface area of ​​the collar arranged in the spiral nozzle assembly is provided with a filter function, so that in case of blockage of the rotating winding in the inlet area, the bypass function ensures a mass flow of the fluid through the spiral flow path, and the filter function filters particles above a predetermined size contained in the fluid from the mass flow of the fluid. Thus, in comparison with prior art devices and methods, the function of the device is ensured not only in the mass flow of fluid through the flow duct of the helical nozzle, but also in the event of blockage of the rotating winding in the inlet region.

[0022] In the event of such a blockage, a bypass function is provided to allow the mass flow of fluid to continue. The filter function retains or filters out particles above a predetermined size contained in the fluid. The filter function is provided in the area of ​​the winding surface of the spiral nozzle winding. If the spiral nozzle assembly is provided with a collar, the filter function is also provided in the area of ​​the collar surface. According to the invention, the filter function is constituted by a number of recesses provided in the winding surface of the winding and / or in the collar surface of the collar. Particles of a corresponding size are filtered out by forming a plurality of recesses of a corresponding shape and size on the winding surface of the winding, the recesses being formed and the filtering being performed in the region of the first turn of the helical winding.

[0023] When a collar is placed on the helical nozzle assembly and a correspondingly sized recess is mounted on the collar surface, the fluid is filtered in the area of ​​the collar at the entrance to the cylindrical cavity. According to the invention, the bypass function for maintaining the mass flow of fluid through the helical nozzle is made possible by a plurality of recesses configured in the winding surface of the winding. If the spiral nozzle becomes blocked in the inlet region of the rotating winding and the mass flow of the fluid is prevented, a bypass function for bypassing the blockage is provided by the recesses in the winding surface of the winding, so that the fluid can flow through the recesses and the subsequent unblocked spiral portion of the flow duct of the spiral nozzle, ensuring the mass flow of the fluid and the function of the spiral nozzle or device. Alternatively, the bypass function for maintaining mass flow of fluid through the helical nozzle can be enabled by a gap configured between the winding surface of the winding and the inner wall of the cylindrical cavity, at least partially along the winding surface.

[0024] In the event of a blockage in the inlet region of the rotating winding that would impede the mass flow of the fluid, a bypass function for circumventing the blockage is instead provided by a gap at least partially configured between the inner wall of the cylindrical cavity and the winding surface, such that the fluid flows through the gap and the subsequent unblocked helical region of the flow duct, ensuring the mass flow of the fluid and the function of the helical nozzle or device. [Effects of the Invention]

[0025] The advantages of the device according to the invention for compressing a gaseous fluid, in particular a refrigerant compressor for a refrigerant circuit of an air conditioning system of a motor vehicle, and of the method for operating the device for compressing a gaseous fluid can be summarized as follows: - ensuring reliable functioning and safe operation by allowing the filtration of particles of critical size from the bypass mass flow and from the fluid mass flow in order to avoid blockages, especially in the region of the spiral nozzle; -No additional parts such as filters or elements are required, so installation takes up minimal space. -Minimal production and operation effort and associated minimal costs. [Brief explanation of the drawings]

[0026] [Figure 1] FIG. 2 is a perspective view showing details of an electrically driven refrigerant compressor. [Figure 2] 2 is an enlarged perspective cross-sectional view of the housing of the refrigerant compressor of FIG. 1. [Figure 3] 3 shows a cross section of the helical nozzle assembly of FIG. 2, in which a plurality of recesses are configured on the winding surface of the winding. [Figure 4] FIG. 10 shows the flow conditions occurring in the inlet region of the spiral nozzle, along with the configuration of the recesses. [Figure 5] FIG. 4 is a perspective view of the helical nozzle assembly of FIG. 3 with a plurality of recesses disposed on the winding surface. [Figure 6] FIG. 6 is an enlarged cross-sectional view of a region of the helical nozzle assembly of FIG. 5. [Figure 7]FIG. 1 is a perspective view of a helical nozzle assembly having a gap disposed in the region of the first revolution, the gap remaining a constant distance; [Figure 8] FIG. 8 is an enlarged cross-sectional view of a region of the helical nozzle assembly of FIG. 7. [Figure 9] FIG. 1 is a perspective view of a helical nozzle assembly positioned in the region of the first revolution and having a gap of decreasing distance. [Figure 10] 10 is an enlarged cross-sectional view of a region of the helical nozzle assembly of FIG. 9. [Figure 11] FIG. 1 is a perspective view of a helical nozzle assembly having a plurality of recesses disposed on the collar surface. [Figure 12a] FIG. 1 is a perspective view showing an outline of a spiral nozzle and collar combination. [Figure 12b] FIG. 1 is a perspective view showing an outline of a spiral nozzle and collar combination. [Figure 12c] FIG. 1 is a perspective view showing an outline of a spiral nozzle and collar combination. [Figure 12d] FIG. 1 is a perspective view showing an outline of a spiral nozzle and collar combination. DETAILED DESCRIPTION OF THE INVENTION

[0027] FIG. 1 is a perspective view showing details of the device 1, in particular the electrically driven refrigerant compressor. The device 1 has a housing 2 configured in a cylindrical cavity 4 in which a helical nozzle assembly 3 is arranged. The main flow direction 5 of the mass flow of the refrigerant flowing through the helical nozzle assembly 3 as a fluid to be compressed is represented by an arrow. Thus, the refrigerant flows from an inlet region 8 towards an end 6 of the cylindrical cavity 4, which is arranged distal from the inlet region 8 and configured in the form of a nozzle. The inlet region 8, configured in the region of a so-called friction plate 7 of the housing 2, is represented by a dashed line. Figure 2 is an enlarged perspective cross-sectional view of the housing 2 of the device 1 of Figure 1. Figure 3 shows a cross-section of the helical nozzle assembly 3 of Figure 2 having a plurality of slot-like recesses 12 configured on the winding surface 11 of the winding 9.

[0028] Blockages due to particles contained in the refrigerant can occur particularly in the inlet region 8 and nozzle end 6 of the cylindrical cavity 4 with the helical nozzle assembly 3 having a helical winding 9 incorporated into the cavity 4. The beginning 13 of the helical winding 9 of the helical nozzle assembly 3 is located in the inlet region 8. The helical winding 9 of the helical nozzle assembly 3 has several turns. Between adjacent turns, a continuous volume is formed as a helical flow duct 10 for the refrigerant, through which the refrigerant passes from the inlet region 8 to the end 6 of the cavity 4. The flow cross section of the flow duct 10 is limited on the one hand by the winding 9 and its base, and on the other hand by the inner wall of the cylindrical cavity 4.

[0029] In the inlet region 8, where a starting end 13 (not shown in detail) of the helical winding 9 of the helical nozzle assembly 3 is located, the winding surface 11 of the winding 9, particularly in the first turn, has a number of recesses 12. The recesses 12, each having a semicircular cross section, extend longitudinally parallel to the longitudinal axis 14 of the cylindrical cavity 4, which corresponds to the longitudinal axis 14 of the helical nozzle assembly 3. With this configuration of the recess 12, when the flow path 10 is blocked in the region of the first rotation of the spiral winding 9 and the refrigerant can no longer flow into the flow path 10, the refrigerant that flows into the spiral nozzle from the inlet region 8 passes through the blocked region of the flow path 10 via the recess 12 configured to have a bypass function, and flows into the flow path 10 in the region of the second rotation following the first circulation.

[0030] This ensures that even if the flow duct 10 is blocked at the inlet region 8 of the spiral nozzle or at the beginning 13 of the spiral winding 9, the coolant will flow through the flow duct 10 of the spiral nozzle to the nozzle end 6 of the cavity 4, thereby ensuring the functionality of the spiral nozzle and therefore of the device 1. The recesses 12 also perform a filtering function for particles contained in the coolant. In this way, the recesses 12 are dimensioned such that particles above a certain size are retained and thus filtered out from the coolant mass flow through the spiral nozzle. Due to this size, the corresponding particles cannot pass through the flow cross section defined by the recesses 12 in communication with the inner wall of the cavity 4.

[0031] 4 is a schematic diagram illustrating the coolant flow conditions occurring in the inlet region 8 of a helical nozzle having a configuration of recesses 12. The various flow paths of the coolant are illustratively indicated by selected flow arrows. Therefore, FIG. 4 shows the coolant flowing into the inlet region 8 from above, showing a portion of the winding 9 with the recess 12 and a portion of the flow duct 10. Due to the blockage of flow path 10, the coolant passes through recess 12 having a bypass function at starting end 13 of winding 9, passes the first turn of winding 9, and flows into flow path 10 downstream of the first turn of winding 9. The refrigerant then flows through the flow duct 10 to the nozzle end 6 of the cylindrical cavity 4 and exits through the spiral nozzle.

[0032] Figure 5 is a perspective view of the helical nozzle assembly 3 of Figure 3 with a plurality of recesses 12 disposed in the winding surface 11 of the winding 9. Figure 6 is an enlarged cross-sectional view of a region of the helical nozzle assembly 3 of Figure 5. The swirl nozzle assembly 3 has turns of the winding 9 which start along the surface of the swirl nozzle assembly 3 and extend spirally at a start portion 13, and swirl flow ducts 10 defined between the turns of the winding 9. To this end, a winding surface 11 of the winding 9, in particular the first turn of the winding 9, is provided with a number of recesses 12. The recesses 12 are each arranged in a section 15 on the winding surface 11 at a distance from one another. Thus, the three sections 15 can in particular each be configured with a plurality of recesses 12. Alternatively, a different number of sections or only one section can be configured. If a single section is configured, it can extend along the winding surface 11 of the entire first turn of the winding 9.

[0033] 6, recess 12 has a rectangular cross section. In an exemplary embodiment, recess 12 is configured to have a width 16 ranging from 0.02 mm to about 0.09 mm and a depth 17 of about 0.09 mm. A two-dimensional filter defined by width 16 and length or depth 17 serves to filter out different sized particle populations in each recess 12. In this way, when the recess 12 with the smallest flow cross section is blocked, different sized particle populations can be filtered out. The configuration of recesses 12 can be varied in number, width, and depth.

[0034] 7 and 8 show a perspective view of the helical nozzle assembly 3 with a gap 18 arranged at a fixed distance 20 in the region of the first turn of the winding 9, and an enlarged cross-sectional view of a partial region of the helical nozzle assembly 3. The first turn of the helical winding 9 has a smaller outer diameter than subsequent portions of the winding 9. Thus, a gap 18 having a constant or unchanging distance 20 is defined between the winding surface 11 of the first turn of the winding 9 and the inner wall 19 of the cylindrical cavity 4 surrounding the helical nozzle assembly 3 along the extension of the first turn. The distance 20 between the winding surface 11 and the inner wall 19 of the cylindrical cavity 4 in the region of the first turn of the winding 9 is in the range of 0.01 mm to 0.20 mm. The gap 18, having a predetermined height as the distance 20 between the winding surface 11 and the inner wall 19 of the cylindrical cavity 4, is narrow enough to allow the coolant to pass through on the one hand and to retain or filter out particles above a predetermined size contained in the coolant from the coolant mass flow on the other hand, thus enabling a bypass function on the one hand and a filtering function of the coolant in the inlet region 8 of the spiral nozzle on the other hand. In this way, if the flow path 10 becomes clogged at the starting end 13 of the spiral winding 9, the refrigerant flows through the gap 18, which functions as a bypass in the inlet region 8, and enters the flow path 10 in the region of the second rotation following the first rotation, and is guided in the direction of the nozzle-shaped end 6, thereby ensuring the function of the spiral nozzle.

[0035] According to FIG. 8, the gap 18, whose distance 20 does not change over its entire length, extends only along the winding surface 11 of the first turn of the winding 9. 9 and 10 are perspective views of a helical nozzle assembly 3 arranged in the region of the first turn of the winding 9 and having a gap 18 with a decreasing distance 20, and an enlarged cross-sectional view of a partial region of the helical nozzle assembly 3. The first turn of the helical winding 9 has an outer diameter that varies along the turn, being smaller than each subsequent portion of the winding 9. Thus, a gap 18 is defined between the winding surface 11 of the first turn of the winding 9 and the inner wall 19 of the cylindrical cavity 4 surrounding the helical nozzle assembly 3, the gap 18 having a distance 20 that varies along the extension of the first turn. The distance 20 between the winding surface 11 in the region of the first turn of the winding 9 and the inner wall 19 of the cylindrical cavity 4 is in the range of 0.001 mm to 0.2 mm.

[0036] Thus, the distance 20 of the gap 18 can be configured to decrease continuously, ramp, or gradually decrease. The gradual decrease in the distance 20 divides the winding surface 11 of the first turn of the winding 9 into sections where the distance 20 is constant. Additionally, by providing a predetermined height for the distance 20 between the winding surface 11 and the inner wall 19 of the cylindrical cavity 4, the gap 18 allows the coolant to pass through, thereby enabling a bypass function for the coolant at the inlet region 8 of the spiral nozzle. Additionally, the gap 18 is configured narrow enough to retain or filter out from the coolant mass flow particles above a predetermined size contained in the coolant, thereby enabling a filter function for the coolant at the inlet region 8 of the spiral nozzle.

[0037] In this way, if the flow path 10 becomes clogged at the starting end 13 of the spiral winding 9, the refrigerant flows through the gap 18, which functions as a bypass in the inlet region 8, and enters the flow path 10 in the region of the second rotation following the first rotation, and is guided in the direction of the nozzle-shaped end 6, thereby ensuring the function of the spiral nozzle. The coolant always flows along the shortest path to the end 6 of the spiral nozzle, so that the coolant flows through the large gap 18 with a distance 20 in each case.

[0038] 10, the gap 18, whose distance 20 varies over its entire length, extends only along the winding surface 11 of the first turn of the winding 9. The gap 18 at the start 13 of the winding 9 has a distance 20a of, for example, 0.2 mm, while the gap 18 at the end of the first turn of the winding 9 has a distance 20b of, for example, 0.001 mm. Furthermore, embodiments are possible in which the configuration of the gap 18, whose distance 20 varies over the length of one turn, is repeated in the second turn of the winding 9, and thus in the first turn of the winding 9 following the first turn. The function of filtering out particulates can be achieved by continuously or stepwise decreasing the distance 20. Since the refrigerant always flows along the shortest path, when the gap 18 with the smallest distance 20 is blocked, the refrigerant will flow through the next larger gap 18.

[0039] FIG. 11 is a perspective view of a helical nozzle assembly 3 having a collar 22 with a plurality of recesses 12 disposed in a collar surface 21 thereof. At the inlet region 8 of the helical nozzle, the helical nozzle assembly 3 has an annular collar 22 with a circumferential collar surface 21 that sealingly abuts the inner wall 19 of the cylindrical cavity 4 (not shown). The collar 22 is positioned in the main flow direction 5 of the refrigerant through the helical nozzle, with the helical nozzle assembly 3 upstream of the beginning 13 of the helical winding 9. The slot-like recesses 12 formed in at least a portion 15 on the circumferential collar surface 21 each extend longitudinally parallel to the longitudinal axis 14 of the cylindrical cavity 4 (not shown), which longitudinal axis 14 corresponds to the longitudinal axis 14 of the helical nozzle assembly 3. The recesses 12 located on the collar surface 21 are sized such that particles contained in the coolant above a predetermined size are retained or filtered from the coolant mass flow, thereby providing a filtering function.

[0040] 12a to 12d are perspective views outlining possible combinations of helical nozzle assembly 3 and collar 22 configurations. Figure 12a shows the helical nozzle assembly 3 of Figure 11, which in the inlet region 8 of the helical nozzle comprises a collar 22 having a plurality of recesses 12 arranged in the circumferential collar surface 21. In addition to the collar 22 having a plurality of recesses 12 arranged in the circumferential collar surface 21, the helical nozzle assembly 3 can also be arranged with a modified winding surface 11 of the winding 9, in particular in the region of the first turn of the winding 9, according to the embodiments according to Figures 7 to 10. FIG. 12b shows a helical nozzle assembly 3 with a configured collar 22 in combination with the configuration of a plurality of recesses 12 on the winding surface 11 of the first turn of the winding 9 according to FIGS.

[0041] FIG. 12c shows a helical nozzle assembly 3 with a collar 22 configured in combination with an arrangement of a gap 18 with a distance 20 that does not vary over the area of ​​the first revolution of the winding 9 according to FIGS. FIG. 12d shows a helical nozzle assembly 3 with a collar 22 configured in combination with a gap 18 configuration with a decreasing distance 20 along the first turn of the winding 9 according to FIGS.

[0042] All embodiments of the recesses 12 and gaps 18 are conceivable for any desired extension on the winding surface 11 from the starting point 13 of the spiral winding 9, and therefore for any desired number of turns. In particular, the size of the recesses 12 and gaps 18 depends on the particles to be filtered and thus on the filtering function. Different shapes of the flow channel cross section can be configured to filter particles of different sizes. Thus, the recess 12 and gap 18 are sized to have minimal effect on the refrigerant mass flow rate as a controlled mass flow rate. Also, various combinations of spiral windings 9 with recesses 12 and collars 22, as well as staged combinations of spiral windings 9 with recesses 12 attached behind various geometric positions, are conceivable. [Explanation of symbols]

[0043] 1 device 2. Housing 3 Spiral nozzle assembly, Spiral nozzle assembly 4 Cylindrical Cavity 5. Main flow direction 6 End, nozzle-shaped end 7 Friction plate 8 Entrance area 9 windings 10 Flow Duct 11 Winding surface 12 Slot-shaped recess 13 Beginning, starting part 14 Longitudinal axis 15 Sections 16 width 17 Depth 18 Gap 19 Inner wall, slot-shaped recess 20 distance 21 Color Surface 22 Color

Claims

1. A device (1) for compressing a gaseous fluid, in particular a scroll compressor for an air conditioning system of a motor vehicle, comprising: It has a housing (2), A cylindrical cavity (4) is defined within the housing (2), A helical nozzle assembly (3) is disposed within the cylindrical cavity (4), The helical nozzle assembly (3) has a helically rotating winding (9) having a winding surface (11), the winding surface (11) is at least partially disposed in sealable contact with the inner wall of the cylindrical cavity (4); A device (1) characterized in that a recess (12) constituting a filter function and a bypass function is arranged on a winding surface (11) of a spirally rotating winding (9) and / or a recess (12) constituting a filter function is arranged on a collar surface (21) of a collar (22) connected to the spiral nozzle assembly (3).

2. 2. The device (1) according to claim 1, characterized in that a plurality of recesses (12) are arranged in the winding surface (11) in a first rotation section (15) of the spirally rotating winding (9).

3. A device (1) for compressing a gaseous fluid, in particular a scroll compressor for an air conditioning system of a motor vehicle, comprising: It has a housing (2), A cylindrical cavity (4) is defined within the housing (2), A helical nozzle assembly (3) is disposed within the cylindrical cavity (4), The helical nozzle assembly (3) has a helically rotating winding (9) having a winding surface (11), the winding surface (11) is at least partially disposed in sealable contact with the inner wall of the cylindrical cavity (4); The device (1) is characterized in that the winding surface (11) of the spirally rotating winding (9) is arranged, in at least one partial region, at a distance (20) from the inner wall of the cylindrical cavity (4), which constitutes a gap (18) for the filter and bypass functions.

4. 4. The device (1) according to claim 3, characterized in that the recesses (12) constituting the filter function are arranged on the collar surface (21) of the collar (22) connected to the spiral nozzle assembly (3).

5. a partial area of ​​the winding surface (11) of the spirally rotating winding (9) having an angle of rotation of the winding (9) ranging from 0° to 720°; the first rotation of the winding (9) comprises an angle ranging from 0° to 360°; 5. The device (1) according to claim 3 or 4, characterized in that in the part (15) of the first turn of the winding (9), as the distance from the start of the winding (9) in the inlet region (8) increases, the gap (18) has a distance (20) to the inner wall of the cylindrical cavity (4) that decreases in the part region or has a constant distance (20).

6. 6. The device (1) according to claim 5, characterized in that the size of the distance (20) of the gap (18) changes in a ramp shape in the range of 0.20 mm to 0 mm, in particular in the range of 0.08 mm to 0 mm, or the distance (20) of the gap (18) has a constant size in the range of 0.01 mm to 0.20 mm, in particular in the range of 0.08 mm to 0.20 mm.

7. 7. Device (1) according to claim 6, characterized in that the recess (12) has a semicircular, rectangular, trapezoidal or triangular cross section.

8. 8. Device (1) according to claim 7, characterized in that the recess (12) has a width (16) in the range of 0.01 mm to 0.02 mm and a depth (17) in the range of 0.008 mm to 0.01 mm.

9. 9. The device (1) according to claim 8, characterized in that a plurality of recesses (12) are arranged distributed on the collar surface (21) in a partial region of the circumference of the collar (22) or over the entire circumference of the collar (22).

10. A method for operating a device (1) for compressing a gaseous fluid, in particular a scroll compressor for an air conditioning system of a motor vehicle, comprising:

1. A method for producing a gas-liquid mixture in a cylindrical cavity (4) defined in a housing (2), the method comprising: disposing a helical nozzle assembly (3) within the cylindrical cavity (4), the helical nozzle assembly (3) having a helically rotating winding (9) having a winding surface (11), the winding surface (11) being disposed at least partially in sealable contact with an inner wall of the cylindrical cavity (4); and causing a mass flow of a gas-liquid mixture within the helical nozzle assembly (3) to pass through a helical flow duct (10) defined during rotation of the winding (9), the method comprising: a bypass function and a filter function are provided in the area of ​​the winding surface (11) of the winding (9) and / or in the area of ​​the collar surface (21) of a collar (22) arranged on the spiral nozzle assembly (3), wherein when the winding (9) is blocked at the inlet area (8), the bypass function ensures a mass flow of fluid through the spiral flow duct (10), and particles contained in the fluid above a predetermined size are filtered out by the filter function.

11. 11. The method according to claim 10, characterized in that the filter function is constituted by a plurality of recesses (12) formed in the winding surface (11) of the winding (9) and / or in the collar surface (21) of the collar (22).

12. 11. The method according to claim 10, wherein the bypass function for maintaining the mass flow of the fluid is constituted by a plurality of recesses (12) formed in the winding surface (11) of the winding (9).

13. 11. The method according to claim 10, characterized in that the bypass function for maintaining the mass flow of the fluid is constituted by a gap (18) formed between the winding surface (11) of the winding (9) and the inner wall of the cylindrical cavity (4) at least partially along the winding surface (11).

14. 14. The method according to claim 13, characterized in that the gap (18) is configured to have a distance (20) that decreases with increasing distance from the start of the winding (9) in the inlet region (8) or a constant distance (20) from the inner wall of the cylindrical cavity (4), respectively.

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