Compressor

Abstract

The invention discloses a compressor. The compressor comprises a static vortex plate; a channel is formed in the movable vortex plate and the movable substrate; a compression chamber; and a back pressure chamber into which a fluid flows from the compression chamber via the passage to establish a first pressure therein; wherein the channel has a port on a first side of the movable base plate, the port is configured to intermittently open and close via a static scroll wall during movement of the movable scroll plate relative to the static scroll plate, the port is located within a second stage compression chamber of a series of compression chambers during opening and has a second pressure at the port, and the port is located within a second stage compression chamber of the series of compression chambers during opening and has a second pressure at the port. When the first pressure is greater than the second pressure, the fluid flows into the compression chamber from the back pressure chamber through the port; when the first pressure is less than the second pressure, the fluid flows from the compression chamber to the back pressure chamber via the port. The backpressure system of the compressor is simplified.

Description

Technical Field

[0001] This application relates to a compressor in which a fluid is pressurized. Background Technology

[0002] A scroll compressor consists of a moving scroll and a stationary scroll. The moving scroll is driven by an eccentric shaft to revolve relative to the fixed stationary scroll without rotating on its own axis, thus forming a compression chamber for compressing the fluid between the moving and stationary scrolls. The side of the moving scroll opposite the stationary scroll has a back pressure chamber. The pressure in the compression chamber exerts a compressive thrust on the moving scroll, while the pressure in the back pressure chamber exerts a back pressure thrust on the moving scroll. During compressor operation, the pressures in the compression chamber and the back pressure chamber are dynamically changing. When there is a difference between the compressive thrust and the back pressure thrust, a thrust imbalance occurs. For example, when the compressive thrust is greater than the back pressure thrust, the end of the moving scroll will detach from the stationary scroll, causing leakage of the compressed fluid. This reduces the compressor's efficiency. Conversely, when the compressive thrust is less than the back pressure thrust, the moving scroll will be pushed by the back pressure thrust, causing its end to press against the stationary scroll. When the compressive thrust is significantly less than the back pressure thrust, the friction between the moving and stationary scrolls becomes too great. The compressor's efficiency will also decrease.

[0003] The back pressure chamber is typically equipped with pathways to introduce pressure from the high-pressure side of the compressor, providing back pressure thrust to counteract the compression thrust in the compressor chamber. Simultaneously, the back pressure chamber also has other pathways for pressure relief to prevent excessive back pressure thrust within it. These pathways constitute the compressor's back pressure system.

[0004] In some designs, the pressure-inducing path is located around the stationary volute plate, communicating with the discharge chamber downstream of the compression chamber. High-pressure fluid, after passing through the stationary volute plate, is introduced into the back pressure chamber via a path on the intermediate plate. In other designs, the high-pressure fluid within the compression chamber is directly utilized. The pressure-inducing path is configured to pass through the volute wall of the moving volute plate. The volute wall on the moving volute plate can be called the moving volute wall. The volute wall on the stationary volute plate is called the stationary volute wall. The stationary and moving volute walls mesh. The pressure-inducing path guides the high-pressure fluid from the top of the moving volute wall through the moving volute wall, and then via a path on the intermediate plate into the back pressure chamber.

[0005] In some designs, the pressure relief path is located on the main shaft; in others, it is located on the intermediate plate; and in still others, the pressure relief path is located on the moving scroll plate, where the fluid in the back pressure chamber is released into the compression chamber.

[0006] Compressor design includes back pressure system design. Researchers need to consider establishing pressure-inducing and pressure-relief channels in relevant components. When the pressure-inducing channel consists of more than two sections, it is also necessary to ensure that the relevant components are in tight contact to avoid leakage that would prevent fluid from being introduced into the back pressure chamber. In addition, the pressure-inducing channel, which is carved through the moving volute wall, has a small diameter and a long length, which places demands on component manufacturing. The longer channel also increases the fluid circulation time in the back pressure system. Summary of the Invention

[0007] One aspect of this application relates to providing a compressor that differs from the pressure-inducing and pressure-reducing designs in the prior art.

[0008] The compressor includes

[0009] A stationary vortex disk having a stationary base plate and a stationary vortex wall, the stationary base plate having a discharge port;

[0010] A moving scroll plate has a moving base plate and a moving scroll wall. The moving base plate is opposite to the stationary base plate. The moving base plate has a first side and a second side. The first side is opposite to the stationary scroll wall. The moving scroll wall engages with the stationary scroll wall. The moving scroll wall extends circumferentially around the center in a manner away from the center of the moving scroll plate. A channel is provided on the moving base plate.

[0011] A compression chamber, located between the stationary substrate and the moving substrate, and comprising a series of compression cavities defined by the stationary vortex wall and the moving vortex wall and varying and moving in volume toward the discharge port, the series of compression cavities including a first-stage compression cavity communicating with the discharge port; and

[0012] A back pressure chamber, located on the second side, through which the fluid flows from the compression chamber into the back pressure chamber to establish a first pressure therein;

[0013] The channel has a port on the first side, the port being configured to open and close intermittently via the stationary volute wall during movement of the moving volute relative to the stationary volute. During opening, the port is located within a second-stage compression chamber of the series of compression chambers and has a second pressure at the port. When the first pressure is greater than the second pressure, fluid flows from the back pressure chamber into the compression chamber via the port; when the first pressure is less than the second pressure, fluid flows from the compression chamber into the back pressure chamber via the port.

[0014] In one embodiment of the compressor, the port is disposed along the outer side of the moving vortex wall; the port is configured to be within an angular range of 166° to 266° between the port and the X-axis in the vortex line generating coordinate system, wherein the vortex line in the vortex line generating coordinate system is fitted to the moving vortex wall.

[0015] In one embodiment of the compressor, the port is disposed along the inner side of the moving vortex wall; the port is configured to be within an angular range of 346° to 446° between the port and the X-axis in the vortex line generation coordinate system, wherein the vortex line in the vortex line generation coordinate system is fitted to the moving vortex wall.

[0016] In one embodiment of the compressor, the distance from the port to the outer or inner side of the moving volute wall is 40% to 50% of the thickness of the moving volute wall at the angular position corresponding to the port.

[0017] In one embodiment of the compressor, the diameter of the port is in the range of 0.5 mm to 2 mm.

[0018] In one embodiment of the compressor, the port is positioned such that the magnitude of the first pressure supplied to the back pressure chamber via the port is within a fluctuation range defined by the minimum and maximum values ​​of the second pressure.

[0019] In one embodiment of the compressor, the channel includes a first channel and a second channel, the first channel having a first port and the second channel having a second port, the first port and the second port being located in two second-stage compression chambers spaced 180° apart.

[0020] In one embodiment of the compressor, the first port is located on the outer side of the moving volute wall, and the second port is located on the inner side of the moving volute wall.

[0021] In one embodiment of the compressor, the first port and the second port are each positioned such that the second pressure at the first port has a first fluctuation segment, and the second pressure at the second port has a second fluctuation segment different from the first fluctuation segment.

[0022] In one embodiment of the compressor, the first port and the second port are formed by drilling holes in the moving substrate.

[0023] This application simplifies the back pressure system, integrating the pressure-inducing and pressure-reducing paths together, thus reducing the number of parts. Furthermore, the channels for pressure induction and decompression are located on the moving base plate; these channels can have a larger diameter and a shorter length, thereby allowing for larger tolerances, reducing machining requirements, and facilitating implementation. This application can reduce the design and manufacturing costs of the compressor.

[0024] This application allows lubricant mixed in the refrigerant to be directly introduced from the compression chamber into the back pressure chamber for lubricating the bearing supporting the moving scroll. The lubricant from the compression chamber has a certain kinetic energy, which can optimize the lubrication conditions of the bearing and give it a longer service life.

[0025] Other aspects and features of this application will become apparent from the following detailed description with reference to the accompanying drawings. However, it should be understood that the drawings are designed for illustrative purposes only and are not intended to limit the scope of this application, as reference should be made to the appended claims. It should also be understood that the drawings are intended only to conceptually illustrate the structures and processes described herein, and are not necessarily drawn to scale unless otherwise indicated. Attached Figure Description

[0026] This application will be more fully understood by referring to the following detailed description of specific embodiments in conjunction with the accompanying drawings, in which the same reference numerals throughout refer to the same elements in the views. Wherein:

[0027] Figure 1 This is a partial schematic diagram of one embodiment of the compressor involved in this application;

[0028] Figure 2 This is an enlarged schematic diagram of one embodiment of the channel in the compressor involved in this application;

[0029] Figure 3 This is a schematic diagram of one embodiment of the moving scroll in the compressor involved in this application;

[0030] Figure 4 This is a schematic diagram of another embodiment of the moving scroll in the compressor involved in this application;

[0031] Figure 5 This is a schematic diagram of another embodiment of the moving scroll in the compressor involved in this application;

[0032] Figure 6 This is a schematic diagram of the dynamic changes of the compression chamber of the compressor involved in this application during one rotation cycle of the main shaft;

[0033] Figure 7 for Figure 6 Enlarged view of part (a);

[0034] Figure 8 A schematic diagram of the design angle of the port located on the outer side of the moving volute wall in the compressor involved in this application;

[0035] Figure 9 A schematic diagram of the design angle of the port located on the inner side of the moving volute wall in the compressor involved in this application; and

[0036] Figure 10This is a schematic diagram of the design dimensions of the ports in the compressor involved in this application. Detailed Implementation

[0037] To help those skilled in the art to accurately understand the subject matter claimed in this application, the specific embodiments of this application are described in detail below with reference to the accompanying drawings.

[0038] Figure 1 This is a partial schematic diagram of one embodiment of the compressor involved in this application. The compressor includes a housing 10, a main shaft 12 disposed within the housing 10, a stationary scroll 14, a moving scroll 16, and an intermediate disk 18. The stationary scroll 14 and the intermediate disk 18 are opposite each other, and the moving scroll 16 is located between the stationary scroll 14 and the intermediate disk 18. The stationary scroll 14 has a stationary base plate 20 and a stationary scroll wall 22, and the moving scroll 16 has a moving base plate 24 and a moving scroll wall 26. After assembly, the stationary base plate 20 and the moving base plate 24 are opposite each other, and the stationary scroll wall 22 and the moving scroll wall 26 are engaged. Between the stationary scroll 14 and the moving scroll 16 is a compression chamber 32, in which fluid is pressurized. The moving base plate 24 has a first side 28 and an opposite second side 30. The first side 28 faces the stationary scroll wall 22, and the second side 30 faces the intermediate disk 18. Between the second side 30 and the intermediate disk 18 is a back pressure chamber 34. The back pressure chamber 34 contains rotating components, such as a bearing 36 supporting the moving scroll 16. The moving scroll 16 is connected to the main shaft 12 via the eccentric shaft 38 and is driven to move by the main shaft 12.

[0039] The stationary vortex wall 22 and the moving vortex wall 26 are each configured as vortex lines extending around the center of their respective vortex disks in a manner away from the center. During the movement of the moving vortex disk 16 relative to the stationary vortex disk 14, the moving vortex wall 26 and the stationary vortex wall 22 come into contact, forming a series of compression chambers within the compression chamber 32. The stationary base plate 20 has a discharge port 41, which communicates with the discharge chamber 42. The compression chambers move from the periphery toward the discharge port 41 and their volumes change. In the series of compression chambers, the compression chambers farther from the discharge port 41 are low-pressure areas, and the compression chambers closer to the discharge port 41 are high-pressure areas, and the volume of the series of compression chambers tends to decrease, and the fluid is gradually pressurized in this series of compression chambers. As indicated by the arrow (black), the fluid entering the compression chamber 32 from the suction side 40 moves with the compression chambers and is pressurized therein until it reaches the center, and is then discharged into the discharge chamber 42 via the discharge port 41.

[0040] After leaving the discharge chamber 42, the fluid passes through the separator 44, and the separated refrigerant gas becomes the compressor's output fluid flow. The remaining portion enters the compressor's lubricant circulation loop, where the fluid does not immediately flow back to the compression chamber. After undergoing external circulation flow in the compressor, the fluid returns to the compressor's suction side 40, mixes with newly drawn refrigerant, and then enters the compression chamber 32.

[0041] A channel 46 is provided on the moving substrate 24. Figure 2 This is an enlarged schematic diagram of one embodiment of the channel. Fluid flows from the compression chamber 32 into the back pressure chamber 34 via the channel 46 to establish a first pressure in the back pressure chamber 34. The channel 46 has a port 50 at a first side 28. Figure 1-2 During the movement of the moving volute 16, port 50 is intermittently opened and closed due to the obstruction of the stationary volute wall 22. Port 50 opens or closes periodically depending on the rotation angle of the main shaft 12. Port 50 has a second pressure during its opening, which varies due to the movement of the compression chamber. When the first pressure is greater than the second pressure, fluid flows from the back pressure chamber 34 into the compression chamber 32 via port 50, as shown by the red arrow in the figure; when the first pressure is less than the second pressure, fluid flows from the compression chamber 32 into the back pressure chamber 34 via port 50, as shown by the blue arrow in the figure.

[0042] In a scroll compressor, the pressure in the compression chamber pushes the moving scroll and stationary scroll apart, creating a gap between the surface of the stationary plate and the top of the moving scroll wall. This gap leads to fluid leakage and reduces compressor efficiency. At this point, the back pressure system comes into play, introducing a certain high pressure into the back pressure chamber to compensate for the pressure difference between the compression chamber and the back pressure chamber. The back pressure can push the moving scroll towards the stationary scroll to eliminate the gap. The channel involved in this application allows fluid to flow bidirectionally within it. Corresponding to one or more rotational angle ranges of the main shaft, the channel serves as a pressure-inducing channel, and corresponding to other one or more rotational angle ranges of the main shaft, the channel serves as a pressure-relief channel.

[0043] The back pressure in the back pressure chamber is provided by the compression chamber, and fluid enters the back pressure chamber through a channel. No additional path is needed to introduce high pressure into the back pressure chamber. The fluid is a mixture of refrigerant and lubricant, thus lubricating the rotating parts in the back pressure chamber. No additional pressure relief path is needed either, as the back pressure is released through this channel, and the fluid returns to the compression chamber.

[0044] In one embodiment, the port 50 is located at a radial position close to the center, rather than on the outer periphery, where medium to high pressure can be obtained, thus providing the required back pressure to the back pressure chamber 34.

[0045] The first pressure and the second pressure are correlated. The desired back pressure is obtained by designing the position of port 50. The first pressure is determined by taking the midpoint of the second pressure at port 50. The fluctuation range of the second pressure between its maximum and minimum values ​​is desirable, because the fluctuation of the second pressure within a certain numerical range means that the magnitude of the first pressure is also within a certain numerical range. Fluid flow in one direction from the compression chamber 32 to the back pressure chamber 34 and in the opposite direction from the back pressure chamber 34 to the compression chamber 32 can be achieved within channel 46. The position of port 50 and the desired back pressure are determined by seeking such a fluctuation range.

[0046] Figure 3 A schematic diagram illustrating one embodiment of a port setting location. Figure 4 This is a schematic diagram illustrating another embodiment of the port setting location. Figure 3 In the illustrated embodiment, port 50 is disposed along the outer side of the moving vortex wall 26. Figure 4 In the illustrated embodiment, port 50 is disposed along the inner side of the moving vortex wall 26.

[0047] Figure 3 and Figure 4 Examples are shown where a port is provided on the moving substrate to enable bidirectional flow of fluid from the compression chamber to the back pressure chamber and from the back pressure chamber to the compression chamber. A greater number of ports, such as two ports, can also be provided on the moving substrate. Figure 5 An embodiment with two ports on the moving substrate 24. The moving substrate 24 has a first port 52 and a first channel (not shown) connecting the compression chamber and the back pressure chamber, and a second port 54 and a second channel (not shown) connecting the compression chamber and the back pressure chamber. The first port 52 and the second port 54 can both be located along the outer side of the moving vortex wall, or both can be located along the inner side of the moving vortex wall, or as... Figure 5 As shown, the first port 52 is disposed along the outer side of the moving vortex wall 26, while the second port 54 is disposed along the inner side of the moving vortex wall 26. In one embodiment, the positions of the two ports are as follows: Figure 3 Examples and Figure 4 Superposition of examples.

[0048] The first port 52 and the second port 54 are formed by drilling holes in the moving substrate 24, which is convenient and easy to implement.

[0049] Figure 6 This diagram illustrates the dynamic changes of the compression chamber within one rotation cycle of the spindle in an embodiment with a two-port moving scroll, where (a) to (h) represent the states at rotation angles of 0°, 45°, 90°, 135°, 180°, 225°, 270°, 315°, and 360°, respectively. To clearly show the port positions and their state changes, only [the diagram showing the port positions and state changes is included]. Figure 6 The middle (a) portion is taken out as Figure 7 As illustrated by the additional reference numerals, the first port 52' is independent of the second port 54'. The opening time of the first port 52' can be staggered from that of the second port 54', or their opening durations (i.e., the corresponding rotation angle ranges) can be different. For example, at a rotation angle of 135°, as shown in (d), the first port located along the outer side of the moving vortex wall is almost completely closed, while the second port located along the inner side of the moving vortex wall has just begun to close. At a rotation angle of 270°, as shown in (g), the first port is open but not fully open, while the second port has been fully opened. In one embodiment, the first port 52' and the second port 54' are configured to be located in different compression chambers 60, 62 during their opening. In another embodiment, the first port 52' and the second port 54' are configured such that the second pressure at the first port 52' has a first fluctuation range, and the second pressure at the second port 54' has a second fluctuation range, which is different from the first fluctuation range. This allows the first pressure supplied to the back pressure chamber to be within a wider numerical range, thereby expanding the operating range of the back pressure system to cope with complex operating conditions.

[0050] The first port 52' and the second port 54' are located within the medium-high pressure compression chamber region during their opening. The compression chamber 47, connected to the discharge port, is the first-stage compression chamber, where the pressure is highest, such as... Figure 7 As shown. The first port 52' and the second port 54' are located in a second-stage compression chamber, i.e., compression chambers 60 and 62 in the figure, during their opening. The first port 52' and the second port 54' are located in two different second-stage compression chambers, which are approximately 180° apart. Figure 6 The compression chamber variation shown in the embodiment illustrates that both ports remain within the second-stage compression chamber during the opening of the first port 52' and the second port 54'. As the compression chamber moves towards the center, the two second-stage compression chambers eventually merge together to form the first-stage compression chamber, at which point the first port 52' and the second port 54' are in the closed state.

[0051] Figure 8 One embodiment involves positioning the port along the outer side of the moving vortex wall. The port is positioned within an angular range of 166° to 266° between the port and the X-axis in the vortex line generation coordinate system. The vortex line 68 in the vortex line generation coordinate system fits the moving vortex wall, extending multiple turns from the base circle 64 at the center along a profile design until its endpoint. The orientation in the coordinate system is defined, with the X-axis used as the reference direction. A port position within the 166° to 266° angular range yields the desired back pressure. Figure 8In the illustrated embodiment, the first port 52” and the second port 54” are respectively positioned at angles α1 of 166° and α2 of 266°. In other embodiments, the first port and the second port can be arranged at any one or more locations within this angle range. The first port 52” and the second port 54” are concentrated in the inner circle of the vortex 68.

[0052] Figure 9 This is one embodiment where the port is positioned along the inner side of the moving vortex wall. The port is positioned within an angular range of 346° to 446° from the X-axis in the vortex line generation coordinate system. The vortex line generation coordinate system and... Figure 8 The coordinate system is the same. Figure 9 In the illustrated embodiment, the first port 52”' and the second port 54”' are respectively positioned at angles where β1 is -14° (i.e., 346°-360°) and β2 is 86° (i.e., 446°-360°). In other embodiments, the first port and the second port can be arranged at any one or more locations within this angle range. Figure 8 Similarly, in the embodiment, the first port 52”' and the second port 54”' are also concentrated in the inner circle of the vortex 68.

[0053] The distances from the first and second ports to the moving vortex wall are related to the thickness of the moving vortex wall at the corresponding angle of that port. For example... Figure 10 As shown in the figure, port 52a corresponds to Figure 8 In the embodiment, the distance d from the first port 52a to the moving vortex wall is set within a proportional range of the corresponding thickness l of the moving vortex wall at this angular position (i.e., 166°), namely 40%l≤d≤50%l. It should be understood that Figure 10 The vortex line is a mathematical model, and its thickness is constant. However, in reality, the thickness of the moving vortex wall is not constant throughout the entire extension range. The distance from port 52a to the moving vortex wall needs to take into account the corresponding thickness of the moving vortex wall at the angular position of this port. In addition, the diameter Ф of port 52a is in the range of 0.5mm≤Ф≤2mm.

[0054] Although specific embodiments of this application have been shown and described in detail to illustrate the principles of this application, it should be understood that this application may be implemented in other ways without departing from such principles.

Claims

1. A compressor, characterized in that: include: A stationary vortex disk (14) having a stationary base plate (20) and a stationary vortex wall (22), the stationary base plate (20) having a discharge port (41); A moving scroll (16) having a moving base plate (24) and a moving scroll wall (26), the moving base plate (24) being opposite to the stationary base plate (20), the moving base plate (24) having a first side (28) and a second side (30), the first side (28) being opposite to the stationary scroll wall (22), the moving scroll wall (26) engaging with the stationary scroll wall (22), the moving scroll wall (26) extending circumferentially around the center in a manner away from the center of the moving scroll (16), and a channel (46) being provided on the moving base plate (24); A compression chamber (32) is located between the stationary substrate (20) and the moving substrate (24), and includes a series of compression cavities defined by the stationary vortex wall (22) and the moving vortex wall (26) and varying and moving in volume toward the discharge port (41). The series of compression cavities includes a first-stage compression cavity communicating with the discharge port (41). A back pressure chamber (34) is located on the second side (30), through which fluid flows from the compression chamber (32) into the back pressure chamber (34) via the channel (46) to establish a first pressure therein; The channel (46) has a port (50) on the first side (28) configured to open and close intermittently via the stationary volute wall (22) during the movement of the moving volute (16) relative to the stationary volute (14). During the opening period, the port (50) is located in the second-stage compression chamber of the series of compression chambers and has a second pressure at the port (50). When the first pressure is greater than the second pressure, the fluid flows from the back pressure chamber (34) into the compression chamber (32) via the port (50); when the first pressure is less than the second pressure, the fluid flows from the compression chamber (32) into the back pressure chamber (34) via the port (50).

2. The compressor according to claim 1, characterized in that: The port is provided along the outer side of the moving vortex wall (26); the port is configured to be within an angular range of 166° to 266° between the port and the X-axis in the vortex line generating coordinate system, wherein the vortex line (68) in the vortex line generating coordinate system is fitted to the moving vortex wall (26).

3. The compressor according to claim 1, characterized in that: The port is provided along the inner side of the moving vortex wall (26); the port is configured to be within an angle range of 346° to 446° between the port and the X-axis in the vortex line generating coordinate system, wherein the vortex line (68) in the vortex line generating coordinate system is fitted to the moving vortex wall (26).

4. The compressor according to claim 2 or 3, characterized in that: The distance (d) from the port to the outer or inner side of the moving vortex wall (26) is 40% to 50% of the thickness (l) of the moving vortex wall (26) at the angular position corresponding to the port.

5. The compressor according to any one of claims 1-3, characterized in that: The diameter (Ф) of the port is in the range of 0.5mm to 2mm.

6. The compressor according to claim 1, characterized in that: The port (50) is positioned such that the magnitude of the first pressure supplied to the back pressure chamber (34) via the port (50) is within a fluctuation range of the second pressure defined by its minimum and maximum values.

7. The compressor according to claim 1, characterized in that: The channel (46) includes a first channel and a second channel. The first channel has a first port (52) and the second channel has a second port (54). The first port (52) and the second port (54) are located in two second-stage compression chambers spaced 180° apart.

8. The compressor according to claim 7, characterized in that: The first port (52) is located on the outside of the moving vortex wall (26), and the second port (54) is located on the inside of the moving vortex wall (26).

9. The compressor according to claim 7, characterized in that: The first port (52) and the second port (54) are respectively positioned such that the second pressure at the first port (52) has a first fluctuation segment, and the second pressure at the second port (54) has a second fluctuation segment different from the first fluctuation segment.

10. The compressor according to any one of claims 7-9, characterized in that: The first port (52) and the second port (54) are formed by drilling on the moving substrate (24).

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