Method for determining position of feed hole of rotary compressor and rotary compressor

Abstract

The invention relates to a method for determining the position of a feed hole of a rotary compressor, comprising the following steps: rotating a rolling piston by a first angle relative to a vane groove, determining a first circumferential range corresponding to the first angle, rotating the rolling piston by a second angle relative to the vane groove, determining a second circumferential range corresponding to the second angle, determining a second circumferential range corresponding to the second angle, determining a third circumferential range in which the rolling piston always closes fluid communication between the filling hole and the cylinder during rotation, and setting the position of the filling hole in an overlapping region within the first circumferential range and the second circumferential range and outside the third circumferential range. The invention also relates to a rotary compressor, which comprises the supplement hole of which the setting position is determined according to the method.

Description

Technical Field

[0001] This invention relates to the field of air conditioning technology, and more particularly to a method for determining the location of the fill hole of a rotary compressor used in an air conditioning device, and a rotary compressor having the fill hole determined by the method. Background Technology

[0002] An air conditioning unit is a device used to regulate indoor air. It typically includes components such as a compressor, an inner heat exchanger, and an outer heat exchanger. These components work together to regulate indoor air to make the environment more comfortable for people inside, for example, providing heated air when the outside temperature is low or cooled air when the outside temperature is high. The compressor is the core component of the air conditioning unit used for heating or cooling indoor air.

[0003] However, when the ambient temperature is too low (e.g., below -10 degrees Celsius), the temperature of the external heat exchanger will also be very low. After running for a long time, frost will form on its surface, affecting heat exchange. At the same time, when the ambient temperature is too low, the density of the medium is lower. In this case, the compressor can absorb a lower mass of medium with the same cylinder volume. As a result, the heating capacity (i.e., air thermal regulation) of the air conditioning equipment is limited and significantly reduced, and it cannot provide high heating capacity at excessively low temperatures. To improve heating capacity when the ambient temperature is too low, a compressor injection enthalpy-increasing mode is introduced. For example, an economizer or flash evaporator is introduced into the air conditioning circuit. The medium leaving the inner heat exchanger (condenser) is processed by the economizer or flash evaporator. The resulting medium-pressure gaseous medium passes through the compressor's injection port without entering the compressor (i.e., injection) for injection compression. The resulting liquid medium is further subcooled by the economizer, which increases the enthalpy difference when the medium absorbs heat and evaporates in the outer heat exchanger (evaporator), thereby increasing the unit heat absorption of the refrigerant during evaporation (i.e., enthalpy increase).

[0004] Alternatively, when the ambient temperature is too high (e.g., above 50 degrees Celsius), the compressor's discharge temperature and the condenser temperature of the external heat exchanger will both be very high. This can cause the compressor motor to overheat, and the excessively high discharge temperature will trigger a protection function, limiting the frequency increase. Consequently, the cooling capacity (i.e., air conditioning) of the air conditioning unit is significantly reduced, failing to provide sufficient cooling at excessively high temperatures. To improve cooling capacity when the ambient temperature is too high, a liquid replenishment mode for the compressor is introduced. The medium-pressure liquid medium leaving the external heat exchanger (condenser) is processed and then replenished into the compressor through a path via the compressor's liquid replenishment port (i.e., liquid replenishment) to cool the compressor and discharge temperature.

[0005] This raises the question of how to set / select / determine the location of the compressor's inlet port for replenishing liquid or gas, and how to effectively control the opening and closing of the compressor's inlet port. Summary of the Invention

[0006] The technical problem to be solved by this invention is how to set / select / determine the position of the inlet hole so that the compressor can operate efficiently and reliably, and at the same time effectively control the opening and closing of the inlet hole with a simple structure and low cost.

[0007] Therefore, according to a first aspect of the present invention, a method for determining the position of a feed port of a rotary compressor is provided, wherein the rotary compressor includes a rolling piston, a cylinder, a feed pipe, a feed port, a suction port, and a vane groove disposed on the cylinder, wherein the rolling piston is rotatable in the cylinder; the feed pipe is in fluid communication with the feed port; the feed port is in fluid communication with the cylinder, wherein the fluid communication between the feed port and the cylinder can be opened or closed by the rotation of the rolling piston;

[0008] In the case where the sliding groove rotates to 0 degrees and the rolling piston rotates clockwise, the method includes:

[0009] - The rolling piston rotates relative to the vane groove by a first angle, wherein the first angle corresponds to the rotation angle that causes the outer side of the rolling piston to rotate to the downstream edge of the intake port for the first time.

[0010] - Determine the first circumferential range of the rolling piston when it rotates to the first angle.

[0011] - The rolling piston rotates relative to the vane groove by a second angle, wherein the second angle corresponds to the rotation angle that compresses the medium in the cylinder to a pressure close to or equal to the pressure of the replenishment medium entering the cylinder from the replenishment port.

[0012] - Determine the second circumferential range of the rolling piston when it rotates to the second angle.

[0013] - Determine the third circumferential range within which the rolling piston always closes the fluid communication between the inlet port and the cylinder during rotation.

[0014] - The location of the filling hole is set in the overlapping area within the first circumferential range and the second circumferential range and outside the third circumferential range.

[0015] This invention employs a rotary compressor, enabling timely / real-time and precise opening and closing of the inlet port via the rotation of the compressor's own rolling piston. This is achieved without the need for additional components (which would cause delays in switching control and affect compressor efficiency) and complex control logic, thus realizing effective control of the inlet port's opening and closing with a simple structure and low cost. Furthermore, since the inlet port's opening and closing is controlled by the rotation of the rolling piston, this application determines the circumferential range of the rolling piston under different corresponding conditions. This allows for the selection of an area where the inlet port is positioned that neither affects the entry of low-pressure medium into the cylinder via the suction port nor the entry of medium-pressure medium into the cylinder via the inlet port (i.e., without causing backflow). This ensures efficient and reliable compressor operation, guaranteeing the quality of the refrigeration / heating cycle.

[0016] According to one aspect of the invention, the method further includes:

[0017] - Determine the third angle based on the intersection of the first and second circumferential ranges, where the third angle is equal to (first angle + second angle) / 2.

[0018] - Determine the fourth circumferential range of the rolling piston corresponding to the third angle.

[0019] - The location of the filling hole is set in the overlapping area and outside the fourth circumferential range.

[0020] According to one aspect of the invention, the method further includes: positioning the insertion hole in the overlapping region at a third angle and close to the intersection of the first circumferential range and the second circumferential range.

[0021] According to one aspect of the invention, when the rolling piston rotates to a second angle, the medium inside the cylinder is compressed to a pressure within the range of 90%-100% of the pressure of the replenishment medium entering the cylinder from the replenishment port.

[0022] According to one aspect of the invention, the inlet hole can be used as both a gaseous medium inlet hole and a liquid medium inlet hole.

[0023] According to one aspect of the invention, the filling hole is provided in the intermediate partition and / or bearing of the rotary compressor.

[0024] According to one aspect of the invention, when the rotary compressor is a dual-cylinder compressor, the inlet hole is disposed in and through an intermediate partition between the upper cylinder and the lower cylinder, and wherein the intermediate partition forms a first inlet passage, the first inlet passage being straight and intersecting the through inlet hole and in fluid communication with the inlet hole, the inlet hole being in fluid communication with the inlet pipe through the first inlet passage.

[0025] According to one aspect of the invention, the upper and lower bearings of the dual-cylinder compressor are respectively provided with inlet holes, and wherein a second inlet passage is in fluid communication with the first inlet passage, and extends upward from the first inlet passage through the intermediate partition and the upper cylinder and into the upper bearing to be in fluid communication with the inlet hole of the upper bearing, and wherein a third inlet passage is in fluid communication with the first inlet passage, and extends downward from the first inlet passage through the intermediate partition and the lower cylinder and into the lower bearing to be in fluid communication with the inlet hole of the lower bearing.

[0026] According to one aspect of the invention, when the rotary compressor is a single-cylinder compressor, the fill hole is provided in the bearing.

[0027] According to a second aspect of the invention, a rotary compressor is provided, the rotary compressor including an inlet hole whose location is determined by the method according to the first aspect of the invention. Attached Figure Description

[0028] The present invention will be further described below with reference to the accompanying drawings and embodiments. In the accompanying drawings:

[0029] Appendix Figure 1 A perspective view of a rotary compressor equipped with an inlet pipe is shown.

[0030] Appendix Figure 2 A flowchart is shown of one embodiment of a method for determining the position of the fill hole of a rotary compressor according to a first aspect of the present invention.

[0031] Appendix Figure 3 A flowchart is shown of one preferred embodiment of a method for determining the position of the fill hole of a rotary compressor according to a first aspect of the present invention.

[0032] Appendix Figure 4 A flowchart is shown of one preferred embodiment of a method for determining the position of the fill hole of a rotary compressor according to a first aspect of the present invention.

[0033] Appendix Figure 5A A schematic cross-sectional view of the rotary compressor according to the invention is shown, with the rolling piston rotating at a first angle, along an axis substantially perpendicular to the crankshaft.

[0034] Appendix Figure 5B A schematic cross-sectional view of the rotary compressor according to the invention is shown, with the rolling piston rotating at a second angle, along an axis substantially perpendicular to the crankshaft.

[0035] Appendix Figure 5CA schematic cross-sectional view of the rotary compressor according to the invention is shown, with the rolling piston at a third angle, along an axis substantially perpendicular to the crankshaft.

[0036] Appendix Figure 5D This illustrates the different circumferential ranges determined by different angles of the rolling piston, the overlap range of the filler holes that can be set, and the additional... Figure 4 A schematic diagram showing the location of the fill hole set by the method shown.

[0037] Appendix Figure 6 An exploded view of an embodiment of a rotary compressor with two cylinders according to the second aspect of the present invention is shown.

[0038] Appendix Figure 7A and 7B The appendix is ​​shown separately. Figure 6 The cross-sectional view of two different implementations of the dual-cylinder compressor is shown basically along the axis parallel to the crankshaft.

[0039] Appendix Figure 8A and 8B A schematic diagram of the heating cycle of an air conditioning device having a rotary compressor according to a second aspect of the present invention is shown.

[0040] Appendix Figure 8C A schematic diagram of the refrigeration cycle of an air conditioning device having a rotary compressor according to the second aspect of the present invention. Detailed Implementation

[0041] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain the present invention, and should not be construed as limiting the present invention.

[0042] See appendix Figure 1 And also refer to the appendix Figure 6According to invention 8, a rotary compressor 100 for use in an air conditioning unit 200 is provided. The rotary compressor 100 includes a rolling piston 10, a cylinder 11, a feed port 12, a feed pipe 13, a suction port 14, a vane groove 15, and vanes 16 slidably configured with the vane groove 15. The rolling piston 10 is rotatable within the cylinder 11; the feed pipe 13 is in fluid communication with the feed port 12, which may be disposed in an intermediate partition 17 and / or a bearing 18 of the rotary compressor and is in fluid communication with the cylinder 11, wherein the fluid communication between the feed port 12 and the cylinder 11 can be opened or closed by the rotation of the rolling piston 10. During operation of the air conditioning unit, a medium-pressure medium can be fed into the cylinder 11 through the feed pipe 13 and feed port 12 according to the rotation of the rolling piston 10, thereby improving the heating capacity of the air conditioning unit in low-temperature environments and the cooling capacity in high-temperature environments.

[0043] The following is an appendix Figure 2 and attached Figures 5A-5D The first embodiment exemplified herein further describes the steps and functions of a method for determining the location of an inlet port of a rotary compressor used in an air conditioning device according to the first aspect of the present invention.

[0044] See appendix Figure 2 And also refer to the appendix Figures 5A-5D For example, taking the center line of the vane groove 15 of the rotary compressor as 0 degrees of rotation and the rolling piston 10 rotating clockwise as an example, the first embodiment of the method for determining the setting position of the filling hole of the rotary compressor used in the air conditioning equipment includes the following steps:

[0045] S1. The rolling piston 10 rotates a first angle A relative to the sliding groove 15 (i.e., rotates 0 degrees), wherein the first angle A corresponds to the rotation angle that causes the outer side of the rolling piston 10 to rotate to the downstream edge 141 of the intake port 14 for the first time (see Appendix). Figure 5AWhen the rolling piston 10 is at the first angle A, that is, when the rolling piston 10 first contacts the downstream edge 141 of the suction port, the region 113 that is disconnected from the suction port 14 is just (beginning) formed / presented in the cylinder 11. Since the gaseous medium entering the cylinder 11 through the suction port 14 is a low-pressure medium, while the medium entering the cylinder 11 through the inlet port 12 is a medium-pressure medium (that is, the pressure of the medium through the inlet port 12 is greater than that of the medium through the suction port 14), it is necessary to establish a region in the cylinder 11 that is disconnected from the suction port before it is allowed to start (at least partially) to open the fluid communication between the inlet port 12 and the cylinder by further rotation of the rolling piston 10, so as to avoid the backflow of the low-pressure gaseous medium drawn in due to the pressure difference, which would reduce the heating / cooling capacity of the air conditioning equipment. Therefore, the inlet port 12 cannot be provided in the region 113.

[0046] S2. Determine the first circumferential range R1 of the rolling piston 10 when it rotates to the first angle A (see Appendix). Figure 5D The filling hole 12 should be located within the first circumferential range R1.

[0047] S3. The rolling piston 10 rotates relative to the sliding vane groove 15 by a second angle B, wherein the second angle B corresponds to the rotation angle that causes the medium in the cylinder 11 to be compressed to a pressure close to (e.g., 90% or more) or equal to the pressure of the replenishment medium entering the cylinder from the replenishment port (see Appendix). Figure 5B As the rolling piston 10 rotates further to the second angle B, the range of region 113 will decrease with the rotation of the rolling piston 10 and the medium in region 113 will be compressed (region 113 can be considered as the compression chamber region in cylinder 11). The introduction of rotation to the second angle B is to avoid the medium pressure in the compression chamber region being compressed to a level greater than the pressure of the medium entering from the inlet hole 12, and to avoid the backflow of the intermediate replenished medium due to the pressure difference (i.e., the pressure in the compression chamber region is greater than the pressure of the medium entering from the inlet hole), which would reduce the heating / cooling capacity of the air conditioning equipment. Therefore, the inlet hole 12 cannot be provided in the range of region 113 that is to be further reduced.

[0048] S4. Determine the second circumferential range R2 of the rolling piston 10 when it rotates to the second angle B (see Appendix). Figure 5D The filling hole 12 should be located within the second circumferential range R2.

[0049] S5. Determine that the rolling piston 10 will always close the fluid communication between the filling hole 12 and the cylinder 11 in the third circumferential range R3 when it rotates; the rolling piston 10 will always occupy a certain range in the cylinder 11 during its rotation, and the filling hole 12 cannot be set in the third circumferential range R3 that is always occupied by the rolling piston 10.

[0050] S6. The position of the filling hole can be selected in the overlapping area within the first circumferential range R1 and the second circumferential range R2 and outside the third circumferential range R3.

[0051] This first embodiment specifically employs a rotary compressor 100, enabling timely / real-time and precise opening and closing of the feed hole 12 through the rotation of the rolling piston 10 inherent in the rotary compressor 100 itself, without the need for additional components (which would cause delays in switching control and affect compressor efficiency) and complex control logic. This achieves effective control of the opening and closing of the feed hole 12 with a simple structure and low cost. Furthermore, this embodiment determines the circumferential range of the rolling piston 10 under different corresponding conditions, namely the first circumferential range R1 (which can be considered as the critical / boundary angle / circumferential range corresponding to the transition of the inlet hole from closed to open), the second circumferential range R2 (which can be considered as the critical / boundary angle / circumferential range corresponding to the transition of the inlet hole from open to closed), and the third circumferential range R3 (which can be considered as the angle / circumferential range corresponding to the inlet hole always being closed), thereby finding the region that will neither affect the entry of low-pressure medium into cylinder 11 via suction port 14 nor affect the entry of medium-pressure medium into cylinder 11 via inlet hole 12 (i.e., will not cause medium backflow) (i.e., the overlapping area within the first circumferential range R1 and the second circumferential range R2 and outside the third circumferential range R3) to set the inlet hole 12 so that the compressor can operate efficiently and reliably to ensure the quality of the refrigeration / heating cycle.

[0052] The following is an appendix Figure 3 and attached Figures 5A-5D The second embodiment exemplarily illustrated further describes the steps and functions of a method for determining the location of a fill hole for a rotary compressor used in an air conditioning device according to the first aspect of the present invention.

[0053] See appendix Figure 3 And also refer to the appendix Figures 5A-5D For example, taking the center line of the vane groove 15 of the rotary compressor as 0 degrees of rotation and the rolling piston 10 rotating clockwise as an example, the second embodiment of the method for determining the setting position of the filling hole of the rotary compressor used in the air conditioning equipment includes the following steps:

[0054] S1. The rolling piston 10 rotates a first angle A relative to the sliding groove 15 (i.e., rotates 0 degrees), wherein the first angle A corresponds to the rotation angle that causes the outer side of the rolling piston 10 to rotate to the downstream edge 141 of the intake port 14 for the first time (see Appendix). Figure 5A When the rolling piston 10 is at the first angle A, that is, when the rolling piston 10 first contacts the downstream edge 141 of the suction port, the region 113 that is disconnected from the suction port 14 is just (beginning) formed / presented in the cylinder 11. Since the gaseous medium entering the cylinder 11 through the suction port 14 is a low-pressure medium, while the medium entering the cylinder 11 through the inlet port 12 is a medium-pressure medium (that is, the pressure of the medium through the inlet port 12 is greater than that of the medium through the suction port 14), it is necessary to establish a region in the cylinder 11 that is disconnected from the suction port before it is allowed to start (at least partially) to open the fluid communication between the inlet port 12 and the cylinder by further rotation of the rolling piston 10, so as to avoid the backflow of the low-pressure gaseous medium drawn in due to the pressure difference, which would reduce the heating / cooling capacity of the air conditioning equipment. Therefore, the inlet port 12 cannot be provided in the region 113.

[0055] S2. Determine the first circumferential range R1 of the rolling piston 10 when it rotates to the first angle A (see Appendix). Figure 5D The filling hole 12 should be located within the first circumferential range R1.

[0056] S3. The rolling piston 10 rotates relative to the sliding vane groove 15 by a second angle B, wherein the second angle B corresponds to the rotation angle that causes the medium in the cylinder 11 to be compressed to a pressure close to (e.g., 90% or more) or equal to the pressure of the replenishment medium entering the cylinder from the replenishment port (see Appendix). Figure 5B As the rolling piston 10 rotates further to the second angle B, the range of region 113 will decrease with the rotation of the rolling piston 10 and the medium in region 113 will be compressed (region 113 can be considered as the compression chamber region in cylinder 11). The introduction of rotation to the second angle B is to avoid the medium pressure in the compression chamber region being compressed to a level greater than the pressure of the medium entering from the inlet hole 13, and to prevent the backflow of the intermediate replenished medium due to the pressure difference (i.e., the pressure in the compression chamber region is greater than the pressure of the medium entering from the inlet hole), thereby reducing the heating / cooling capacity of the air conditioning equipment. Therefore, the inlet hole 12 cannot be provided in the range of region 113 that is to be further reduced.

[0057] S4. Determine the second circumferential range R2 of the rolling piston 10 when it rotates to the second angle B (see Appendix). Figure 5D The filling hole 12 should be located within the second circumferential range R2.

[0058] S5. Determine that the rolling piston 10 will always close the fluid communication between the filling hole 12 and the cylinder 11 in the third circumferential range R3 when it rotates; the rolling piston 10 will always occupy a certain range in the cylinder 11 during its rotation, and the filling hole 12 cannot be set in the third circumferential range R3 that is always occupied by the rolling piston 10.

[0059] S6. Determine the third angle C based on the intersection of the first circumferential range R1 and the second circumferential range R2, where the third angle C is equal to (first angle A + second angle B) / 2; that is, the third angle C is determined by connecting the intersection point of the first circumferential range R1 and the second circumferential range R2.

[0060] S7. Determine the fourth circumferential range R4 corresponding to the third angle C of the rolling piston 10.

[0061] S8. The position of the filling hole 12 is set within the overlapping area RR within the first circumferential range R1 and the second circumferential range R2 and outside the third circumferential range R3 and the fourth circumferential range R4.

[0062] In this second embodiment, by introducing a third angle C and a corresponding fourth circumferential range R4 of the rolling piston 10, the range that can be used to set the inlet hole 12 is reduced. This allows the inlet hole 12 to be opened earlier than the setting range of the first embodiment by further rotation of the rolling piston 10 after a region in the cylinder 11 that is disconnected from the suction hole 14 is established during the rolling of the rolling piston 10. Furthermore, the inlet hole 12 can be closed later (while avoiding the medium pressure in the compression chamber region being compressed to a level greater than the pressure of the medium-pressure medium entering from the inlet hole 12). This allows the medium-pressure medium to be supplied more efficiently through the inlet hole, enabling the compressor to operate more efficiently and reliably to ensure the quality of the refrigeration / heating cycle.

[0063] See appendix Figure 4 And also refer to the appendix Figures 5A-5D For example, taking the center line of the vane groove 15 of the rotary compressor as 0 degrees of rotation and the rolling piston 10 rotating clockwise as an example, the third embodiment of the method for determining the setting position of the filling hole of the rotary compressor used in the air conditioning equipment includes the following steps:

[0064] S1. The rolling piston 10 rotates a first angle A relative to the sliding groove 15 (i.e., rotates 0 degrees), wherein the first angle A corresponds to the rotation angle that causes the outer side of the rolling piston 10 to rotate to the downstream edge 141 of the intake port 14 for the first time (see Appendix). Figure 5AWhen the rolling piston 10 is at the first angle A, that is, when the rolling piston 10 first contacts the downstream edge 141 of the suction port, the region 113 that is disconnected from the suction port 14 is just (beginning) formed / presented in the cylinder 11. Since the gaseous medium entering the cylinder 11 through the suction port 14 is a low-pressure medium, while the medium entering the cylinder 11 through the inlet port 12 is a medium-pressure medium (that is, the pressure of the medium through the inlet port 12 is greater than that of the medium through the suction port 14), it is necessary to establish a region in the cylinder 11 that is disconnected from the suction port before it is allowed to start (at least partially) to open the fluid communication between the inlet port 12 and the cylinder by further rotation of the rolling piston 10, so as to avoid the backflow of the low-pressure gaseous medium drawn in due to the pressure difference, which would reduce the heating / cooling capacity of the air conditioning equipment. Therefore, the inlet port 12 cannot be provided in the region 113.

[0065] S2. Determine the first circumferential range R1 of the rolling piston 10 when it rotates to the first angle A (see Appendix). Figure 5D The filling hole 12 should be located within the first circumferential range R1.

[0066] S3. The rolling piston 10 rotates relative to the sliding vane groove 15 by a second angle B, wherein the second angle B corresponds to the rotation angle that causes the medium in the cylinder 11 to be compressed to a pressure close to (e.g., 90% or more) or equal to the pressure of the replenishment medium entering the cylinder from the replenishment port (see Appendix). Figure 5B As the rolling piston 10 rotates further to the second angle B, the range of region 113 will decrease with the rotation of the rolling piston 10 and the medium in region 113 will be compressed (region 113 can be considered as the compression chamber region in cylinder 11). The introduction of rotation to the second angle B is to avoid the medium pressure in the compression chamber region being compressed to a level greater than the pressure of the medium entering from the inlet hole 13, and to prevent the backflow of the intermediate replenished medium due to the pressure difference (i.e., the pressure in the compression chamber region is greater than the pressure of the medium entering from the inlet hole), thereby reducing the heating / cooling capacity of the air conditioning equipment. Therefore, the inlet hole 12 cannot be provided in the range of region 113 that is to be further reduced.

[0067] S4. Determine the second circumferential range R2 of the rolling piston 10 when it rotates to the second angle B (see Appendix). Figure 5D The filling hole 12 should be located within the second circumferential range R2.

[0068] S5. Determine that the rolling piston 10 will always close the fluid communication between the filling hole 12 and the cylinder 11 in the third circumferential range R3 when it rotates; the rolling piston 10 will always occupy a certain range in the cylinder 11 during its rotation, and the filling hole 12 cannot be set in the third circumferential range R3 that is always occupied by the rolling piston 10.

[0069] S6. Determine the third angle C based on the intersection of the first circumferential range R1 and the second circumferential range R2, where the third angle C is equal to (first angle A + second angle B) / 2; that is, the third angle C is determined by connecting the intersection point of the first circumferential range R1 and the second circumferential range R2.

[0070] S7. Determine the fourth circumferential range R4 corresponding to the third angle C of the rolling piston 10.

[0071] S8. Determine the overlapping area within the first circumferential range R1 and the second circumferential range R2, and outside the third circumferential range R3 and the fourth circumferential range R4.

[0072] S9. The position of the filling hole is set in the overlapping area at a third angle C and close to the intersection of the first circumferential range R1 and the second circumferential range R2.

[0073] In this third embodiment, by introducing a third angle C and arranging the inlet hole 12 as close as possible to the intersection of the first circumferential range R1 and the second circumferential range R2, the opening and closing of the inlet hole 12 can be as close as possible to the critical / boundary condition / situation. That is, after a region in the cylinder 11 that is disconnected from the fluid communication with the suction port 14 is established, the rolling piston 10 will open the inlet hole 12 more immediately / as early as possible after further rotation compared to the first and second embodiments, and (while avoiding the medium pressure in the compression chamber region being compressed to a level greater than the pressure of the medium-pressure medium entering from the inlet hole 12) close the inlet hole 12 as late as possible. This allows the medium-pressure medium to be supplied more efficiently through the inlet hole, enabling the compressor to operate more efficiently and reliably, thus ensuring the quality of the refrigeration / heating cycle.

[0074] See Appendix below. Figure 7A and 7B And also refer to the appendix Figure 6 Two different embodiments of the twin-cylinder compressor in the rotary compressor 100 according to the second aspect of the present invention will be described.

[0075] As attached Figure 7AAs shown, in the first embodiment of the dual-cylinder compressor, the dual-cylinder compressor includes an upper cylinder 111 and a lower cylinder 112, and an intermediate partition 17 located between the upper and lower cylinders. The inlet hole 12 is positioned within the intermediate partition 17 according to the method steps described above, and is provided through the intermediate partition 17. A first inlet passage 171, which is linear, is formed in the intermediate partition 17. This first inlet passage 171 intersects with and is in fluid communication with the throughlet hole 12. The throughlet hole 12 is in fluid communication with the inlet pipe 13 through the first inlet passage 171. Thus, the medium-pressure medium in the air conditioning circulation path can be supplied to the upper and lower cylinders through the inlet pipe 13 and via the first inlet passage 171 from the throughlet hole 12 based on the rotation control of the rolling piston 10 (without causing undesirable backflow of the medium entering through the suction hole and the medium entering through the inlet hole, i.e., without causing loss of air conditioning heating / cooling capacity). In this embodiment, by setting the filling hole 12 to pass through the intermediate partition 17, both the upper and lower cylinders can be filled with medium-pressure medium through the filling hole.

[0076] As attached Figure 7BAs shown, in the second embodiment of the twin-cylinder compressor, in addition to providing a fill hole in the intermediate partition as in the first embodiment, fill holes 12 can also be provided on the upper bearing 181 and lower bearing 182 of the twin-cylinder compressor at positions determined according to the method steps described above; in order to fluidly communicate with the fill hole provided on the upper bearing 181, a zigzag-shaped second fill passage 172 is also provided, which is fluidly communicated with the first fill passage 171, and from the first fill passage 171... 1. Extends upward through the intermediate partition 17 and the upper cylinder 111 and enters the upper bearing 181 to fluidly communicate with the filling hole 12 of the upper bearing. In order to fluidly communicate with the filling hole provided on the lower bearing 182, a zigzag-shaped third filling passage 173 is also provided. The third filling passage 173 is fluidly communicated with the first filling passage 171, and extends downward from the first filling passage through the intermediate partition 17 and the lower cylinder 112 to enter the lower bearing 182 to fluidly communicate with the filling hole 12 of the lower bearing. Thus, the medium-pressure medium in the air conditioning circulation can be supplied from the replenishment pipe 13 via the first replenishment passage 171 through the replenishment hole 12 penetrating the middle partition and based on the rotation control of the rolling piston 10 (without causing undesirable backflow of the medium entering through the suction hole and the medium entering through the replenishment hole, i.e. without causing loss of air conditioning heating / cooling capacity) to the upper cylinder 111 from below and the lower cylinder 112 from above, and from the first replenishment passage 171 and via the second replenishment passage 172 through the replenishment hole 12 arranged in the upper bearing 181 from above and from the first replenishment passage 171 and via the third replenishment passage 173 through the replenishment hole 12 arranged in the lower bearing 182 from below. In this embodiment, by providing filling holes on both the intermediate partition and the upper / lower bearings, that is, by providing filling holes on both the upper and lower sides of the rolling piston 10, the medium-pressure medium can be filled from both the upper and lower sides of the rolling piston through the filling holes, thereby ensuring that the force acting on the rolling piston is balanced when the medium is filled, which reduces the friction between the rolling piston and the bearing / intermediate partition, thereby improving the reliability of the compressor.

[0077] Alternatively, the rotary compressor 100 according to the second aspect of the invention may also relate to an embodiment of a single-cylinder compressor. In the embodiment of the single-cylinder compressor, the fill hole may be provided on the bearing at a position range determined according to the method steps described above, and its specific arrangement may be considered to be substantially similar to the arrangement mentioned in the second embodiment of the twin-cylinder compressor described above, and will not be repeated here.

[0078] As can be seen from the above description of different embodiments of the compressor, the method for determining the position of the fill hole according to the present invention can be applied to different types of rotary compressors, such as twin-cylinder / single-cylinder compressors and vertical / horizontal compressors.

[0079] Appendix Figure 8A and 8B Schematic diagrams of heating cycles for two different embodiments of an air conditioning device 200 according to a second aspect of the present invention are shown, wherein the air conditioning device 200 includes a compressor 100 provided with an inlet port determined by the method according to a first aspect of the present invention. An economizer 101 (see attached diagram) is introduced into the circuit of the air conditioning device. Figure 8A ) or flash evaporator 102 (see appendix) Figure 8B The medium leaving the inner heat exchanger, i.e., the condenser 103, after being processed by the economizer 101 or the flash evaporator 102, forms a medium-pressure gaseous medium that is fed into the compressor 100 through the feed pipe 13 via a path (i.e., feed gas) for feed gas compression. The liquid medium formed, due to the processing of the economizer or the flash evaporator, has an increased enthalpy difference during heat absorption and evaporation in the outer heat exchanger, i.e., the evaporator 104, thereby increasing the unit heat absorption of the refrigerant (i.e., enthalpy increase) to improve the heating capacity of the air conditioning equipment when the ambient temperature is too low.

[0080] Appendix Figure 8C A schematic diagram of the refrigeration cycle of an air conditioning device 200 according to a second aspect of the present invention is shown, wherein the air conditioning device 200 includes a compressor 100 provided with a fill port determined according to the method of a first aspect of the present invention. The medium leaving the outer heat exchanger, i.e., the condenser 103, passes through the expansion valve 105, and the resulting medium-pressure liquid medium is replenished into the compressor via a path through the fill pipe 13 of the compressor 100 through the fill port (i.e., liquid replenishment) to cool the compressor and the exhaust temperature, thereby improving the cooling capacity of the air conditioning device when the ambient temperature is too high.

[0081] In the heating and cooling cycle as described above, both gaseous and liquid media can be fed into the compressor through the inlet holes determined by the method according to the first aspect of the invention, thereby avoiding the need to provide separate inlet holes for gaseous and liquid media and simplifying the structure of the compressor.

[0082] In the description of the invention, it should be understood that the terms "top", "upper", "bottom", "lower", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation structure and operation. Therefore, they should not be construed as limiting the invention.

[0083] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance. Therefore, a feature specified as "first" or "second" may explicitly or implicitly include one or more of that feature.

[0084] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can combine, change, modify, substitute and vary the above embodiments within the scope of the present invention.

Claims

1. A method for determining the location of the inlet port of a rotary compressor, wherein, The rotary compressor includes a rolling piston, a cylinder, a feed pipe, a feed hole, a suction port, and a vane groove disposed on the cylinder. The rolling piston is rotatable in the cylinder. The feed pipe is in fluid communication with the feed hole. The feed hole is in fluid communication with the cylinder. The fluid communication between the feed hole and the cylinder can be opened or closed by the rotation of the rolling piston. In the case where the sliding groove rotates to 0 degrees and the rolling piston rotates clockwise, the method includes: - The rolling piston rotates relative to the vane groove by a first angle, wherein the first angle corresponds to the rotation angle that causes the outer side of the rolling piston to rotate to the downstream edge of the intake port for the first time. - Determine the first circumferential range of the rolling piston when it rotates to the first angle. - The rolling piston rotates relative to the vane groove by a second angle, wherein the second angle corresponds to the rotation angle that compresses the medium in the cylinder to a pressure close to or equal to the pressure of the replenishment medium entering the cylinder from the replenishment port. - Determine the second circumferential range of the rolling piston when it rotates to the second angle. - Determine the third circumferential range within which the rolling piston always closes the fluid communication between the inlet port and the cylinder during rotation. - The location of the filling hole is set in the overlapping area within the first circumferential range and the second circumferential range and outside the third circumferential range.

2. The method according to claim 1, wherein, The method also includes: - Determine the third angle based on the intersection of the first and second circumferential ranges, where the third angle is equal to (first angle + second angle) / 2. - Determine the fourth circumferential range of the rolling piston corresponding to the third angle. - The location of the filling hole is set in the overlapping area and outside the fourth circumferential range.

3. The method according to claim 2, wherein, The method further includes: positioning the insertion hole in the overlapping area at a third angle and close to the intersection of the first circumferential range and the second circumferential range.

4. The method according to any one of claims 1 to 3, wherein, When the rolling piston rotates to the second angle, the medium inside the cylinder is compressed to a pressure within the range of 90%-100% of the pressure of the replenishment medium entering the cylinder from the replenishment port.

5. The method according to any one of claims 1 to 3, wherein, This inlet can be used as an inlet for both gaseous and liquid media.

6. The method according to any one of claims 1 to 3, wherein, The fill hole is located in the middle partition and / or bearing of the rotary compressor.

7. The method according to claim 6, wherein, When the rotary compressor is a dual-cylinder compressor, the fill hole is located in the intermediate partition between the upper and lower cylinders and extends through the intermediate partition. The intermediate partition has a first replenishment passage, which is straight and intersects with the through replenishment hole and is in fluid communication with the replenishment hole. The replenishment hole is in fluid communication with the replenishment pipe through the first replenishment passage.

8. The method according to claim 7, wherein, The upper and lower bearings of this dual-cylinder compressor are also equipped with fill holes, and The second inlet passage is in fluid communication with the first inlet passage, and extends upward from the first inlet passage through the intermediate partition and the upper cylinder to enter the upper bearing so as to be in fluid communication with the inlet hole of the upper bearing. The third inlet passage is in fluid communication with the first inlet passage, and extends downward from the first inlet passage through the intermediate partition and the lower cylinder and into the lower bearing to be in fluid communication with the inlet hole of the lower bearing.

9. The method according to claim 6, wherein, When the rotary compressor is a single-cylinder compressor, the fill hole is located in the bearing.

10. A rotary compressor, wherein, The rotary compressor includes an inlet hole whose location is determined according to the method of any one of the preceding claims.

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