Scroll compression mechanism and scroll compressor

Abstract

The present disclosure provides a scroll compression mechanism and a scroll compressor, the scroll compression mechanism comprising: a moving scroll; and a fixed scroll assembly comprising a fixed scroll and a cover plate, the fixed scroll comprising a fixed scroll end plate, the cover plate being fixed to one side of the fixed scroll end plate such that a central high-pressure recess capable of being in fluid communication with a central compression chamber is defined between the cover plate and the fixed scroll end plate, a back pressure chamber being provided on the side of the cover plate facing away from the fixed scroll, the fixed scroll assembly further being provided with a medium-pressure passage, the medium-pressure passage being in fluid communication between an intermediate compression chamber and the back pressure chamber, a sealing reinforcement structure defining a sealing reinforcement region being provided between the cover plate and the fixed scroll end plate, the medium-pressure passage passing through the sealing reinforcement region, thereby preventing leakage of working fluid from the central high-pressure recess to the medium-pressure passage. The scroll compression mechanism according to the present disclosure is capable of preventing wear failure of the scroll compression mechanism, prolonging the service life of the scroll compression mechanism and improving its use performance.

Description

TECHNICAL FIELD

[0001] The present disclosure relates to the technical field of scroll compressors, and more particularly, to a scroll compressor and a scroll compressor. BACKGROUND

[0002] The contents of this section merely provide background information related to the present disclosure, which can not constitute the prior art.

[0003] Compressors can be applied to application systems requiring different pressures, such as air conditioning systems, refrigeration systems, etc., and thus, the discharge pressure (the maximum pressure in the compression chamber) of the compression chamber can be greater than the required pressure of the specific application system, i.e., over-compression can occur. In order to reduce or prevent over-compression of working fluid, a compressor having a variable volume ratio function has been developed.

[0004] In the compressor having the variable volume ratio function, generally, the fixed scroll adopts a split type design including a cover plate. In the split type fixed scroll, there is a problem in that the scroll compressor is easily worn out and fails, and thus, there is a demand for providing an improved scroll compressor. SUMMARY

[0005] One object of one or more embodiments of the present disclosure is to provide a scroll compressor in which wear and failure of the scroll compressor can be prevented, the service life of the scroll compressor can be extended, and the use performance thereof can be improved.

[0006] Another object of one or more embodiments of the present disclosure is to provide a scroll compressor in which the assembly process of the compressor can be simplified, and the compatibility of the cover plate and the seal can be improved.

[0007] According to an aspect of the present disclosure, there is provided a scroll compressor, including: a moving scroll; and a fixed scroll assembly including a fixed scroll and a cover plate, the fixed scroll being engaged with the moving scroll to define a series of compression chambers including a central compression chamber and an intermediate compression chamber, the fixed scroll including a fixed scroll end plate, the cover plate being fixed to one side of the fixed scroll end plate such that a central high-pressure recess capable of being in fluid communication with the central compression chamber is defined between the cover plate and the fixed scroll end plate, a back pressure chamber being provided on a side of the cover plate facing away from the fixed scroll, the fixed scroll assembly further being provided with a medium-pressure passage fluidly connecting the intermediate compression chamber and the back pressure chamber, characterized in that a seal reinforcement structure is provided between the cover plate and the fixed scroll end plate, the seal reinforcement structure defining a seal reinforcement region, the medium-pressure passage passing through the seal reinforcement region, thereby preventing working fluid from leaking from the central high-pressure recess to the medium-pressure passage.

[0008] According to an aspect of the present disclosure, the mid-pressure passage includes a mid-pressure exhaust hole provided in the fixed scroll end plate and a cover plate exhaust hole provided in the cover plate, the seal reinforcement structure includes a perforated fastener provided with a longitudinal through hole, the perforated fastener passes through the cover plate exhaust hole and is fastened in the mid-pressure exhaust hole, such that a seal reinforcement region is defined at and around the perforated fastener, and such that the perforated fastener allows the intermediate compression chamber and the back pressure chamber to be in fluid communication via the longitudinal through hole while fastening the cover plate to the fixed scroll end plate.

[0009] According to an aspect of the present disclosure, the seal reinforcement structure further includes a seal gasket or a seal ring provided at least around the perforated fastener.

[0010] According to an aspect of the present disclosure, the fixed scroll assembly is further provided with a main fastener arranged radially outward of the mid-pressure passage and fixing the cover plate to the fixed scroll end plate.

[0011] According to an aspect of the present disclosure, the seal reinforcement structure includes a first seal ring provided radially inward of the mid-pressure passage and a second seal ring provided radially outward of the mid-pressure passage, such that the seal reinforcement region is defined between the first seal ring and the second seal ring.

[0012] According to an aspect of the present disclosure, the fixed scroll assembly is further provided with a main fastener, the main fastener and the mid-pressure passage are both located in the seal reinforcement region and the main fastener fixes the cover plate to the fixed scroll end plate.

[0013] According to an aspect of the present disclosure, in the seal reinforcement region, one or both of a surface of the cover plate facing the fixed scroll end plate and a surface of the fixed scroll end plate facing the cover plate is provided with an annular gas guide groove, the mid-pressure passage includes a mid-pressure exhaust hole provided in the fixed scroll end plate and a cover plate exhaust hole provided in the cover plate, the mid-pressure exhaust hole and the cover plate exhaust hole are both open to the gas guide groove.

[0014] According to an aspect of the present disclosure, the main fastener is a plurality and is arranged uniformly in a circumferential direction.

[0015] According to an aspect of the present disclosure, the portion of the mid-pressure passage provided in the fixed scroll end plate includes a first axial section connected with the intermediate compression chamber, a second axial section open to a surface of the fixed scroll end plate facing the cover plate, and a transverse connecting section connecting the first axial section and the second axial section.

[0016] According to an aspect of the present disclosure, a variable volume ratio orifice is provided in the fixed scroll end plate, and a one-way valve for selectively opening and closing the variable volume ratio orifice is provided in the central high pressure recess.

[0017] According to another aspect of the present disclosure, a scroll compressor including a scroll compression mechanism is provided.

[0018] The compressor structure according to the present disclosure can prevent wear failure of the scroll compression mechanism, prolong the service life of the scroll compression mechanism, and improve the use performance thereof. BRIEF DESCRIPTION OF DRAWINGS

[0019] The drawings described herein are for purposes of illustration only and are not intended to limit the scope of the present disclosure in any way.

[0020] Figure 1 FIG. 1 is a cross-sectional view schematically illustrating a compressor according to a comparative example;

[0021] Figure 2 FIG. 2 is a cross-sectional view schematically illustrating a fixed scroll assembly of the compressor according to the comparative example;

[0022] Figure 3 FIG. 3 is an exploded perspective view schematically illustrating the fixed scroll assembly of the compressor according to the comparative example;

[0023] Figure 4a and 4b FIG. 4 is a cross-sectional view and an exploded perspective view schematically illustrating a fixed scroll assembly of a compressor according to a first embodiment of the present disclosure, respectively;

[0024] Figure 5 FIG. 5 is a top view schematically illustrating a seal alternative arrangement of the fixed scroll assembly of the compressor according to the first embodiment of the present disclosure;

[0025] Figure 6 FIG. 6 is a cross-sectional view schematically illustrating a fixed scroll assembly of a compressor according to a second embodiment of the present disclosure;

[0026] Figure 7 FIG. 7 is an exploded perspective view schematically illustrating the fixed scroll assembly of the compressor according to the second embodiment of the present disclosure;

[0027] Figure 8 FIG. 8 schematically illustrates a fool-proof design of a fixed scroll assembly of a compressor according to a comparative example; and

[0028] Figure 9 FIG. 9 is a cross-sectional view schematically illustrating a fixed scroll assembly of a compressor according to a third embodiment of the present disclosure. DETAILED DESCRIPTION

[0029] The following description of the various embodiments of the present disclosure is merely exemplary in nature and is in no way intended to limit the present disclosure, its application, or uses. The same numbers are used in the various drawings to represent the same or similar components. Thus, the construction of the same numbers will not be repeatedly described.

[0030] Reference will now be made to Figures 1-3 A compressor having a variable displacement ratio function according to a comparative example will be described, wherein Figure 1 A cross-sectional view of a compressor according to a comparative example is schematically shown; Figure 2 A cross-sectional view of a fixed scroll assembly of a compressor according to a comparative example is schematically shown; and Figure 3 An exploded perspective view of a fixed scroll assembly of a compressor according to a comparative example is schematically shown.

[0031] As Figure 1 shown, the scroll compressor 1 includes a substantially closed casing 10. The casing 10 can be composed of a substantially cylindrical body portion, a top cover 12 provided at one end of the body portion, and a bottom cover 16 provided at the other end of the body portion. A partition 14 is provided between the top cover 12 and the body portion to divide the internal space of the casing 10 into a fluid suction chamber 11 and a fluid discharge chamber 13. The space between the partition 14 and the top cover 12 constitutes the fluid discharge chamber 13, and the space between the partition 14, the body portion, and the bottom cover constitutes the fluid suction chamber 11.

[0032] A scroll compression mechanism and a driving mechanism for driving the scroll compression mechanism are provided in the casing 10. The compression mechanism sucks in fluid from the fluid suction chamber 11 of the casing 10 and discharges the fluid after compression into the fluid discharge chamber 13 of the casing 10. Referring to Figure 1 , the compression mechanism can include, for example, a fixed scroll assembly 30 and an orbiting scroll 20. The orbiting scroll 20 includes an orbiting scroll end plate and an orbiting scroll wrap formed in a spiral shape on one side of the orbiting scroll end plate. As Figure 2 more clearly shown, the fixed scroll assembly 30 includes a fixed scroll end plate 32 and a fixed scroll wrap 34 formed in a spiral shape on one side of the fixed scroll end plate 32, the fixed scroll end plate 32 including a main discharge port 50 formed at a substantially central position of the fixed scroll end plate, a variable displacement ratio port 52 located radially outward of the main discharge port 50, and a medium pressure discharge hole 54 located radially outward of the variable displacement ratio port 52.

[0033] As Figure 2 shown, the fixed scroll assembly 30 further includes a cover plate 100 provided on the side of the fixed scroll end plate 32 opposite the wrap 34 and fixed to the fixed scroll end plate 32. In particular, as Figure 3As shown, the cover plate 100 is formed with a plurality of fixation holes 128, and the fixed scroll end plate 32 is formed with a plurality of fixation holes 114 corresponding to the fixation holes 128, so that main fasteners 124 such as screws can extend through the fixation holes 128 and 114 to secure the cover plate 100 to the fixed scroll assembly 30. The fasteners 124 can be provided in a plurality and uniformly distributed on the cover plate to apply uniform fastening force. As shown, Figure 2 As shown, the cover plate 100 is further formed with a cover plate exhaust hole 140 corresponding to the intermediate pressure exhaust hole 54, and the working fluid in the intermediate compression chamber C3 can flow to the back pressure chamber 70 through an intermediate pressure passage including the intermediate pressure exhaust hole 54 and the cover plate exhaust hole 140. The fixation holes 114 are provided on the outer periphery of the fixed scroll end plate 32, and a central high pressure recess 36 is provided radially inward of the fixation holes 114, and as shown, Figure 2 As shown, the central high pressure recess 36 is in fluid communication with the main exhaust port 50 and selectively in fluid communication with the variable volume ratio port 52, i.e. the working fluid in the central high pressure recess 36 is at a high pressure exhaust pressure. The variable volume ratio port 52 is provided with a one-way valve Figure 2 Only a single variable volume ratio port is shown, but it is understood that a plurality of variable volume ratio ports can be formed as needed. The one-way valve allows fluid to flow from the compression chamber to the central high pressure recess 36, and prevents fluid from flowing from the central high pressure recess 36 to the compression chamber. The one-way valve can include a valve flap covering the variable volume ratio port and a valve stop preventing excessive deformation of the valve flap. The one-way valve can be secured to the fixed scroll end plate 32 by fasteners such as screws.

[0034] As shown, Figure 2 The cover plate 100 includes an inner annular wall 110 (also referred to as a first annular wall) and an outer annular wall 130 (also referred to as a second annular wall) and a connecting portion 150 connecting the inner annular wall and the outer annular wall. The inner annular wall 110 encircles a central chamber 120 which is in fluid communication with the central high pressure recess 36. The back pressure chamber 70 is formed by the space surrounded by the inner annular wall 110, the outer annular wall 130 and the connecting portion 150 and is closed by a sealing assembly provided therein. As shown, Figure 2 As shown, the back pressure chamber 70 is in fluid communication with the intermediate compression chamber C3 through the intermediate pressure exhaust hole 54, thereby forming a force pressing the fixed scroll assembly 30 towards the orbiting scroll 20, and the pressure in the back pressure chamber 70 can effectively press the fixed scroll assembly 30 and the orbiting scroll 20 together.

[0035] During the operation of compressor 1, the working fluid is drawn into the compression mechanism and compressed as it flows from the outermost radial position to the innermost radial position. That is, the working fluid pressure is lowest in the outermost radial compression chamber, highest in the central compression chamber C1 located at the center of the vortex, and has an intermediate pressure between the maximum and minimum pressure in the intermediate compression chamber C3 located between the outermost and innermost radial positions. The compressed fluid is discharged through the main exhaust port 50 to the central high-pressure recess 36 of the fixed vortex end plate 32. However, in an over-compressed state, the compression mechanism compresses the working fluid to a pressure higher than required by the application system (e.g., air conditioning system, cold storage system, cryogenic refrigeration system, etc.), thus causing the compressor to perform unnecessary work under over-compression conditions. To prevent over-compression, the fluid can be discharged to the central high-pressure recess 36 before reaching the innermost radial position through the variable volume ratio orifice 52. Specifically, when the pressure in a particular compression chamber is greater than or equal to the pressure required by the application system, the one-way valve can open the variable volume ratio orifice 52 to allow the fluid in the compression chamber to be discharged directly without overcompression.

[0036] like Figure 2 As shown, the central high-pressure recess 36 is in fluid communication with the central cavity 120 and has a higher pressure equal to the compressor discharge pressure. The space on the radially outer side of the fixed scroll end plate 32 is located in the fluid suction cavity and has a lower pressure equal to the compressor suction pressure. The back pressure cavity 70 is in fluid communication with the intermediate pressure exhaust port 54 and has an intermediate pressure between the discharge pressure and the suction pressure. To prevent the high-pressure fluid in the central high-pressure recess 36 from leaking into the low-pressure space through the interface between the cover plate 100 and the fixed scroll end plate 32, a sealing gasket 60 is provided between the cover plate 100 and the fixed scroll end plate 32. An exhaust port 64 and a fixing hole 66 are formed on the sealing gasket 60, and the exhaust port 64 and the fixing hole 66 are aligned with the intermediate pressure exhaust port 54 and the fixing hole 114 of the fixed scroll end plate 32, respectively.

[0037] like Figure 3 As specifically shown, multiple fasteners 124 secure the cover plate 100 and the sealing gasket 60 to the fixed scroll assembly 30. The tightening force applied by the fasteners 124 clamps the sealing gasket 60 between the fixed scroll end plates 32 of the fixed scroll assembly 30, thereby sealing the interface between them. However, in actual use of the compressor, there is a problem of scroll failure due to wear between the fixed scroll and the moving scroll, which adversely affects the service life and compression performance of the compressor.

[0038] Through repeated research, the inventors of this application discovered that this problem is caused by the relative position of the fasteners and the intermediate-pressure vent. Specifically, on the one hand, fasteners such as screws are typically arranged on the outer periphery of the fixed scroll end plate 32 to provide sufficient space for installing a one-way valve to selectively open the variable volume ratio orifice, and to ensure that the fasteners do not obstruct the normal operation of the one-way valve. On the other hand, in order to provide sufficient back pressure to the back pressure chamber 70, the intermediate-pressure vent 54 is typically located radially inward relative to the fasteners (or the fixing holes for the fasteners). This results in a radial offset between the fasteners and the intermediate-pressure vent. After simulation experiments and calculations, the inventors of this application found that this radial offset between the fasteners and the intermediate-pressure vent causes insufficient tightening force on a portion of the sealing gasket, thus failing to effectively seal the interface between the fixed scroll end plate and the cover plate, resulting in fluid leakage. Specifically, the sealing gasket near the medium-pressure vent is not tightened enough, which causes the high-pressure working fluid in the recess to leak into the medium-pressure vent 54 and further into the back pressure chamber 70. The leaked high-pressure fluid causes the pressure in the back pressure chamber 70 to increase, which in turn causes a significant increase in the axial pressure of the fixed vortex assembly 30 pressing against the moving vortex 20, resulting in wear between the vortices.

[0039] To address the aforementioned problems, the inventors have conceived an improved compressor structure that enhances the seal between the reinforcing cover plate and the fixed scroll end plate, thereby preventing scroll wear caused by leakage of high-pressure working fluid. Specifically, a sealing reinforcement structure is provided in the contact area between the cover plate and the fixed scroll end plate. This sealing reinforcement structure defines a sealing reinforcement area, through which a medium-pressure channel, including a medium-pressure exhaust port, passes. This reinforces the seal of the medium-pressure exhaust port, preventing working fluid from leaking from the central high-pressure recess through the contact area to the back pressure chamber.

[0040] Figure 4a and Figure 4bCross-sectional views and exploded perspective views of the fixed scroll assembly of the compressor according to the first embodiment of this disclosure are shown. The compressor according to the first embodiment of this disclosure is substantially the same in construction as the compressor according to the comparative example, and will not be described again here. The only difference is that the compressor of the first embodiment of this disclosure further includes a perforated fastener 80 fixed in the intermediate pressure exhaust port 54. The perforated fastener 80 can be fixed in the intermediate pressure exhaust port 54 in any suitable manner, such as threaded connection, interference fit, etc. The perforated fastener 80 has a longitudinal through hole that is in fluid communication with the intermediate pressure exhaust port 54 and the back pressure chamber 70. The fastening force applied by the perforated fastener 80 tightly clamps the surrounding sealing gasket between the cover plate and the fixed scroll end plate. The perforated fastener 80 and the sealing gasket constitute a sealing reinforcement structure. In this way, the perforated fastener 80 can define a sealing reinforcement area at its own position and in its surrounding area. Within this sealing reinforcement area, the perforated fastener 80 acts directly on the intermediate pressure vent 54, thus significantly increasing the fastening force on the sealing gasket located near the intermediate pressure vent 54. This prevents high-pressure working fluid from leaking into the intermediate pressure vent 54 and subsequently into the back pressure chamber 70, avoiding wear failure of the fixed and moving scrolls. Therefore, an improved solution with a simple structure, high operability, and low cost is provided. Furthermore, the fastening force applied by the fastener can be further increased by increasing the size of the fastener (e.g., increasing the size of the fastening head).

[0041] In the compressor of the first embodiment of this disclosure, the seal is not limited to Figure 3 The integral sealing gasket 60 shown is not applicable; however, it can take any other suitable form. Figure 5 A top view of a fixed scroll assembly with an alternative sealing gasket is shown, wherein some components of the fixed scroll have been removed for clarity. (Refer to...) Figure 5Instead of a gasket, a first O-ring 62b surrounding the intermediate pressure vent 54 and a second O-ring 64b disposed between the intermediate pressure vent 54 and the fixing hole 114 can be used. In this case, the sealing reinforcement structure includes a first O-ring 62b disposed around the intermediate pressure channel in the contact area between the cover plate and the fixed scroll end plate, thereby defining a sealing reinforcement area at the first O-ring 62b and its inner region. Although an embodiment with a gasket or sealing ring disposed between the cover plate and the fixed scroll end plate is shown here, it is understood that when the gap between the cover plate and the fixed scroll end plate is very small, the gasket or sealing ring can be omitted, and the seal between the cover plate and the fixed scroll end plate can be maintained directly by using a perforated fastener 80 and a main fastener 124. Furthermore, it should be noted that although the central high-pressure recess 36 is schematically depicted on the top surface of the fixed scroll end plate 32 in this application, those skilled in the art should understand that this disclosure is not limited thereto. For example, the recess can be alternatively formed on the underside of the cover plate 100, while the top surface of the fixed scroll end plate 32 is formed as a plane. Alternatively, recesses can be formed on both the top surface of the fixed scroll end plate 32 and the underside of the cover plate 100. The goal is to provide a high-pressure exhaust region between the cover plate and the fixed scroll end plate, with a pressure equal to the exhaust pressure of the scroll compressor. This high-pressure exhaust region is in fluid communication with the main exhaust port 50 and selectively in fluid communication with the variable volume ratio orifice 52.

[0042] Below, we will refer to Figures 6-7 The constant scroll assembly 30a of the compressor according to the second embodiment of the present disclosure will be described in detail.

[0043] The fixed vortex assembly 30a has a structure that is basically the same as that of the fixed vortex assembly 30 according to the first embodiment and the comparative example; the differences will be described below only. Figure 6 As shown, the portion of the intermediate pressure channel located on the fixed scroll end plate 32a includes a first axial section 542a, a second axial section 544a, and a transverse connecting section 546a. The first axial section 542a extends along the axial direction of the compressor and connects to the intermediate compression chamber C3. The second axial section 544a extends axially to the surface of the fixed scroll end plate 32a facing the cover plate 100 and forms an intermediate pressure exhaust port 54a. The intermediate pressure exhaust port 54a connects to the fixing hole 114 (e.g., ...). Figure 7The radial distances from the axis of the fixed scroll to the intermediate pressure exhaust port 54a and the fixed port 114 are approximately the same, therefore the intermediate pressure exhaust port 54a and the fixed port 114 are located in the same annular region. The transverse connecting section 546a can extend in a transverse direction perpendicular to the axial direction of the compressor and connect the first axial section 542a and the second axial section 544a. The first axial section 542a extends through the fixed scroll end plate 32a and has a plug 210 at its end near the central high pressure recess 36 to prevent working fluid from leaking from the intermediate pressure exhaust passage to the central high pressure recess 36. The transverse connecting section 546a has an outer end that extends through the fixed scroll end plate 32a. The intersection point of the transverse connecting section 546a and the second axial section 544a is P. The transverse connecting section 546a has a plug 220 radially outside the intersection point P to prevent working fluid from leaking from the intermediate pressure exhaust passage to the fluid suction chamber. Since the portion of the transverse connecting section 546 located radially inside the intersection P is necessary for forming the medium-pressure exhaust passage, while the portion located radially outside the intersection P is an invalid part caused by the processing technology, it is preferable that the plug 320 be placed in the invalid part near the intersection P to reduce the clearance volume of the compressor.

[0044] Reference Figure 7 An annular air guide groove 310 is formed on the fixed vortex end plate, and the fixing hole 114 and the medium-pressure exhaust hole 54a are located in the air guide groove 310. A first sealing groove 320 and a second sealing groove 330 are respectively provided on the radially outer and inner sides of the air guide groove 310 to accommodate the first sealing ring 410 and the second sealing ring 420. The first sealing groove 320 and the second sealing groove 330 can be arranged adjacent to the air guide groove 310. The sealing rings can exemplary include O-rings and any other suitable gaskets.

[0045] The cover plate 100a has a basically the same structure as the cover plate 100. The only difference is that the radial distance from the cover plate exhaust hole 140a and the fixed hole 128 to the axis of the fixed vortex is the same.

[0046] Reference Figure 6 and Figure 7 In the fixed vortex assembly 30a according to the second embodiment of the present disclosure, the working fluid in the intermediate compression chamber C3 flows from the first axial section 542a to the transverse connecting section 546a, and then flows through the second axial section 544a into the air guide groove 310. Finally, the working fluid passes through the air guide groove 310 and through the cover plate exhaust hole 140a. Figure 6 (Not shown) enters the back pressure chamber 70. The first sealing ring 410 located on the radially inner side prevents the high-pressure working fluid in the central high-pressure recess 36 from flowing to the air guide groove 310, and the second sealing ring 420 located on the radially outer side prevents the medium-pressure working fluid in the air guide groove 310 from flowing to the suction pressure chamber.

[0047] In the fixed vortex according to the second embodiment of this disclosure, the first sealing ring 410 and the second sealing ring 420 are arranged in the area surrounding the main fastener 124, which can apply sufficient tightening force to the first and second sealing rings and the area between them. Therefore, the sealing reinforcement structure including the first and second sealing rings defines a sealing reinforcement area between the first and second sealing rings. A medium-pressure channel including a medium-pressure vent 54a is located within this sealing reinforcement area. Specifically, as Figure 7 As shown, since the radial distance between the intermediate pressure vent 54a and the fixed hole 114 and the axis of the fixed vortex is the same and there is no radial offset, the intermediate pressure vent 54a can be located in the sealing reinforcement area between the first sealing ring and the second sealing ring. In this way, the intermediate pressure channel including the intermediate pressure vent 54a passes through the sealing reinforcement area, thereby preventing the working fluid from leaking from the central high pressure recess through the contact area to the back pressure chamber by strengthening the seal of the intermediate pressure vent, thereby preventing wear failure of the fixed vortex and the moving vortex.

[0048] Furthermore, in the fixed scroll according to the second embodiment of this disclosure, since the working fluid in the intermediate compression chamber is introduced into the back pressure chamber 70 using the annular air guide groove 310, the intermediate pressure exhaust port 54a of the fixed scroll end plate 32a and the cover plate exhaust port 140a of the cover plate can be positioned arbitrarily in the circumferential direction without the need for misalignment design, simplifying the assembly process and improving the versatility of the cover plate and sealing gasket. Specifically, in the fixed scroll according to the comparative example and the first embodiment, in order to introduce the working fluid in the intermediate compression chamber into the back pressure chamber 70, the intermediate pressure exhaust port 54 of the fixed scroll end plate 32, the exhaust port 64 of the sealing gasket 60, and the cover plate exhaust port of the cover plate 100 need to be aligned to form an intermediate pressure channel. For this purpose, corresponding misalignment design needs to be provided on the sealing gasket 60 and the fixed scroll end plate 32. Figure 8 An example of a foolproof design for the gasket and stator end plate in a compressor according to a comparative example is shown, such as... Figure 8As shown, the sealing gasket 60 has a foolproof feature 68, and the fixed scroll end plate 32 has a corresponding foolproof feature 38 to align the intermediate pressure exhaust port 54 of the fixed scroll end plate 32 with the exhaust port in the sealing gasket 60. Since the positions of the intermediate pressure exhaust ports differ for different fixed scrolls, the cover plate and sealing gasket are individually designed for specific fixed scrolls to match different intermediate pressure exhaust port designs, making the cover plate and sealing gasket non-interchangeable. Furthermore, during the scroll concept design phase, the position of the intermediate pressure exhaust port is constantly adjusted and changed to improve compressor performance and reduce scroll axial force. Each adjustment requires custom-made sealing gaskets and cover plates, significantly increasing design costs and slowing down new product development. Simultaneously, as new products are developed, the number of cover plates and sealing gaskets increases, and these cover plates and sealing gaskets have very similar external characteristics, easily leading to material mixing and affecting normal production. In the fixed vortex according to the second embodiment of the present disclosure, since the medium-pressure exhaust holes of the fixed vortex and the cover plate can be arranged at any position in the circumferential direction without needing to be aligned with each other, the same set of cover plates and sealing gaskets can be applied to fixed vortices with different medium-pressure exhaust holes. Thus, the position of the medium-pressure exhaust hole of the fixed vortex can be adjusted very conveniently without replacing the sealing gaskets and cover plates.

[0049] Figure 9 A cross-sectional view of the fixed vortex assembly 30b according to the third embodiment of the present disclosure is shown. The fixed vortex assembly 30b is structurally similar to the fixed vortex assembly 30a according to the second embodiment of the present disclosure, except that the air guide groove 310b is formed on the lower side of the cover plate 100b, and the top surface of the fixed vortex end plate 32 is formed as a plane, which facilitates the spatial layout of the upper plane of the fixed vortex and reduces the processing and manufacturing difficulty of the fixed vortex. Those skilled in the art should understand that the present disclosure is not limited thereto, and the air guide groove can also be formed on both the top surface of the fixed vortex end plate 32 and the lower side of the cover plate 100.

[0050] Although various embodiments and variations of this disclosure have been specifically described above, those skilled in the art should understand that this disclosure is not limited to the specific embodiments and variations described above, but may include various other possible combinations and arrangements. Other variations and modifications can be implemented by those skilled in the art without departing from the spirit and scope of this disclosure. All such variations and modifications fall within the scope of this disclosure. Moreover, all components described herein can be replaced by other technically equivalent components.

Claims

1. A scroll compressor mechanism, comprising: Dynamic vortex (20); as well as A fixed vortex assembly includes a fixed vortex (30) and a cover plate (100). The fixed vortex engages with the moving vortex to define a series of compression chambers, including a central compression chamber (C1) and an intermediate compression chamber (C3). The fixed vortex includes a fixed vortex end plate (32). The cover plate is fixed to one side of the fixed vortex end plate (32) such that a central high-pressure recess (36) capable of fluid communication with the central compression chamber is defined between the cover plate and the fixed vortex end plate. A back pressure chamber (70) is provided on the side of the cover plate opposite to the fixed vortex. The fixed vortex assembly also includes an intermediate pressure channel that fluidly communicates the intermediate compression chamber with the back pressure chamber. The feature is that a sealing reinforcement structure is provided between the cover plate and the fixed vortex end plate, the sealing reinforcement structure defining a sealing reinforcement area, and the intermediate pressure channel passing through the sealing reinforcement area, thereby preventing the working fluid from leaking from the central high-pressure recess to the intermediate pressure channel, and The intermediate pressure channel includes an intermediate pressure vent (54) disposed in the fixed vortex end plate and a cover plate vent (140) disposed in the cover plate. The sealing reinforcement structure includes a perforated fastener (80) with a longitudinal through hole. The perforated fastener passes through the cover plate vent (140) and is fastened in the intermediate pressure vent, thereby defining the sealing reinforcement area at and around the perforated fastener. The perforated fastener also allows the intermediate compression chamber and the back pressure chamber to be fluidly connected via the longitudinal through hole while fastening the cover plate to the fixed vortex end plate.

2. The scroll compression mechanism according to claim 1, characterized in that, The sealing reinforcement structure also includes at least a sealing gasket or sealing ring disposed around the perforated fastener.

3. The vortex compression mechanism according to claim 1, characterized in that, The fixed vortex assembly is also provided with a main fastener (124), which is arranged radially outside the medium pressure channel and fixes the cover plate to the fixed vortex end plate.

4. The scroll compression mechanism according to any one of claims 1 to 3, characterized in that, The portion of the medium-pressure channel disposed in the fixed vortex end plate includes a first axial section connected to the intermediate compression chamber, a second axial section opening into the surface of the fixed vortex end plate facing the cover plate, and a transverse connecting section connecting the first axial section and the second axial section.

5. The scroll compression mechanism according to any one of claims 1 to 3, characterized in that, A variable volume ratio orifice (52) is provided in the fixed vortex end plate, and a one-way valve for selectively opening and closing the variable volume ratio orifice is provided in the central high pressure recess.

6. A scroll compressor, characterized in that, The scroll compressor includes a scroll compression mechanism according to any one of claims 1 to 5.

Images