CN211343341U

CN211343341U - Scroll compressor having a plurality of scroll members

Info

Publication number: CN211343341U
Application number: CN201921542047.5U
Authority: CN
Inventors: 张琼宇; 刘轩
Original assignee: Emerson Climate Technologies Suzhou Co Ltd
Current assignee: Copeland Suzhou Co Ltd
Priority date: 2018-09-19
Filing date: 2019-09-17
Publication date: 2020-08-25
Anticipated expiration: 2029-09-17
Also published as: CN110925195A; WO2020057535A1

Abstract

A scroll compressor may include a first scroll member and a second scroll member, a first scroll blade of the first scroll member meshing with a second scroll blade of the second scroll member to form a series of compression pockets including a suction pocket, a plurality of intermediate pockets, and a discharge pocket, a bypass passage extending through a first end plate of the first scroll member. One end of the bypass passage communicates with the exhaust passage via a bypass port and the other end communicates with the intermediate cavity, the position of the bypass port being offset in the radial direction from the position at which the bypass passage communicates to the intermediate cavity. The configuration of the bypass passage allows for increased freedom in the design of the variable volume ratio of the scroll compressor.

Description

Scroll compressor having a plurality of scroll members

Technical Field

The present disclosure relates to the field of scroll compressors, and more particularly, to scroll compressors having variable volume ratios.

Background

This section provides background information related to the present disclosure, which is not necessarily prior art.

A climate control system, such as a heat pump system, a refrigeration system, or an air conditioning system, may include a fluid circuit having an outdoor heat exchanger, an indoor heat exchanger, an expansion device disposed between the indoor and outdoor heat exchangers, and one or more compressors that circulate a working fluid (e.g., a refrigerant) between the indoor and outdoor heat exchangers. Efficient and reliable operation of the compressor is desirable to ensure that the climate control system in which the compressor is installed is able to effectively and efficiently provide cooling and/or heating effects as needed. Scroll compressors with Variable Volume Ratio (VVR) are commonly used in such systems to match the pressure ratio of the compressor to the operating pressure required by the system to avoid over-compression.

Scroll compressors are known as typical positive displacement compressors. The compression mechanism of a scroll compressor generally includes a fixed scroll member and an orbiting scroll member, scroll blades of the fixed scroll member and the orbiting scroll member cooperate with each other to form a series of compression pockets to compress a working fluid (also referred to as a working fluid, such as a gaseous refrigerant), and a compressed high-pressure gas is discharged to a discharge passage and thus a discharge pressure region via a discharge passage.

In order to realize a variable volume ratio, a bypass passage for communicating the intermediate compression cavity with the exhaust passage is provided in an end plate of the fixed scroll member, the bypass passage is provided with a check valve (bypass valve) at each of outlets communicating with the exhaust passage, and pressures of the exhaust passage and the exhaust pressure region correspond to a working pressure of the system. When the required operating pressure of the system is low, the pressure of the intermediate cavity is sufficient to open the one-way valve and discharge the medium-pressure gas, which has not been sufficiently compressed, to the discharge pressure region, the compressor operating at a low volume ratio; when the required operating pressure of the system is high, the bypass valve remains closed and the compressor operates at a high volume ratio.

However, since the area of the exhaust passage is limited, the degree of freedom in designing the bypass passage is low when the exhaust passage and the outlet of the bypass passage, and thus the bypass valve, are disposed within the limited spatial range of the exhaust passage. Not only is the capacity of adjusting the design volume ratio limited, but the design of the bypass valve itself is also limited. In addition, the axially extending intermediate pressure gas inlet of the bypass passage needs to communicate with the axially extending intermediate pressure gas outlet, and therefore the position of the intermediate pressure gas inlet is also limited, which also limits the adjustability of the design volume ratio.

SUMMERY OF THE UTILITY MODEL

A general summary of the disclosure is provided in this section and is not a comprehensive disclosure of the full scope of the disclosure or all of the features of the disclosure.

It is an object of the present disclosure to provide a variable volume ratio scroll compressor capable of avoiding system efficiency loss due to over-compression.

It is another object of the present disclosure to provide a scroll compressor having a high degree of freedom in design of a variable volume ratio, particularly, a wider range of design of the volume ratio, to improve the operating efficiency of a system including the compressor.

According to one aspect of the present disclosure, there is provided a scroll compressor, including: a first scroll member including a first end plate and a first scroll blade extending from the first end plate; a second scroll member including a second end plate and a second scroll blade extending from the second end plate, the second scroll blade meshing with the first scroll blade to form a series of compression pockets including a suction pocket, a plurality of intermediate pockets, and a discharge pocket. The first end plate includes a bypass passage extending therethrough, one end of the bypass passage communicating with an exhaust passage via a bypass port and the other end communicating with the intermediate cavity, the bypass port being located at a position offset in a radial direction from a position at which the bypass passage communicates to the intermediate cavity.

In some embodiments, the bypass passage may include a first section and a second section in communication with each other, the first section leading to the intermediate cavity and the second section leading to the exhaust passage.

In some embodiments, the bypass passage may further comprise a laterally extending connecting section connecting the first and second sections.

In some embodiments, the first end plate may include a first annular wall surrounding a first region on a side opposite the first scroll blade, the first annular wall defining the exhaust passage. The first end plate may further include a discharge passage extending through the first end plate, one end of the discharge passage communicating with the exhaust channel via a discharge port and the other end communicating with the discharge pocket. The discharge port and the bypass port are both disposed within the first region.

In some embodiments, a bypass valve may be provided at the bypass port, the bypass valve being a one-way valve.

In some embodiments, the bypass passages may include a first set of bypass passages including one or more first bypass passages and a second set of bypass passages including one or more second bypass passages.

In some embodiments, in the first set of bypass passages, the first section and the second section may be one or more, and the first section and the second section may be directly connected by one of the connecting sections. In the second group of bypass passages, the first section and the second section are one or more, and the first section and the second section can be directly communicated through one connecting section.

In some embodiments, the first set of bypass passages includes a plurality of first bypass passages, and among the plurality of first bypass passages, the connection section may include a first connection section directly communicating with part or all of the first section, and a second connection section directly communicating with the remaining first section, the first connection section, and the second section. The second set of bypass passages may include a plurality of second bypass passages, and among the plurality of second bypass passages, the connection section may include a first connection section directly communicating with part or all of the first sections, and a second connection section directly communicating with the remaining first sections, the first connection section, and the second sections.

In some embodiments, the one or more first bypass passages may comprise a respective one or more of the second sections, and the one or more second bypass passages may comprise a respective one or more of the second sections.

In some embodiments, the one or more first bypass passages may share a single second section, and the one or more second bypass passages may share a single second section.

In some embodiments, the one or more first bypass passages and the one or more second bypass passages may share one said second section and one said bypass port.

In some embodiments, a discharge valve may be provided at the discharge port and a bypass valve may be provided at the bypass port, the discharge valve and the bypass valve being one-way valves.

In some embodiments, the bypass valve may be provided separately from the discharge valve. Alternatively, the bypass valve may be provided as an integrated valve with the discharge valve in which at least one of a valve plate, a valve member, a valve stop and a biasing member is a common member.

In some embodiments, the first section may be disposed radially outward of the first region in a radial direction away from the second section.

In some embodiments, the connection section may include an active volume section and an inactive volume section, the inactive volume section extending from the location of the opening of the connection section to a communication location in communication with the other section, the scroll compressor may further include a choke for eliminating the inactive volume section.

In some embodiments, one end face of the plug may include a tool engagement recess for engagement by a tool to insert the plug into the dead volume section.

In some embodiments, the connecting section may include an internal thread over the entire length of the dead volume section, the plug may be in the shape of an externally threaded stud, the length of the plug is less than the length of the dead volume section, and the dead volume section may be isolated from the active volume section by screwing the plug into the dead volume section and fixing the plug at a position where the dead volume section is adjacent to the active volume section.

In some embodiments, the connecting section may be formed with an internal thread only at a position of the opening thereof, the plug is in the shape of a stepped column and includes a first cylindrical portion having an external thread formed on an outer peripheral surface thereof for engagement with the internal thread and a second cylindrical portion having a diameter slightly smaller than the first cylindrical portion, the second cylindrical portion being set to a length capable of filling the dead volume section.

In some embodiments, the first end plate may further include a second annular wall radially outward of the first annular wall, the first and second annular walls defining a backpressure chamber therebetween, and the backpressure chamber communicating with one of the intermediate pockets via a backpressure passage extending through the first end plate, the intermediate pocket communicating with the backpressure passage being different from the intermediate pocket communicating with the bypass passage.

In some embodiments, the discharge passage may communicate with a discharge pressure region of the scroll compressor via a one-way valve.

The scroll compressor with variable volume ratio according to the present disclosure enables improved variable volume ratio performance and significantly improved efficiency of the overall system incorporating the compressor by improved design of the bypass passage adding the intermediate transverse section. Meanwhile, according to the scroll compressor disclosed by the invention, the design freedom of the size, the shape, the position and the like of the bypass passage can be improved without increasing the size of the compressor, and further, the adjustment capacity of the volume ratio and the design freedom of the bypass valve can be improved, so that the exhaust strategy of the bypass passage can be more conveniently designed and the design requirements of various bypass valves can be met. The energy efficiency and the applicability of the compressor are greatly improved, and the compressor has a wide application prospect.

Drawings

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

FIG. 1 is a schematic longitudinal cross-sectional view of an exemplary compressor having a variable volume ratio;

FIG. 2 is a partially cut-away exploded perspective view illustrating the non-orbiting scroll member and bypass valve of the compressor shown in FIG. 1;

FIG. 3a is a perspective view of a bypass passage according to an embodiment of the present disclosure, and FIG. 3b is a schematic longitudinal cross-sectional view of a non-orbiting scroll member to which the bypass passage shown in FIG. 3a is applied;

FIG. 4a is a perspective view of a bypass passage according to another embodiment of the present disclosure, and FIG. 4b is a schematic longitudinal cross-sectional view of a non-orbiting scroll member to which the bypass passage shown in FIG. 4a is applied;

FIG. 5 is a perspective view, partially in section, of the non-orbiting scroll member shown in FIG. 4 b;

FIG. 6 is a transverse cross-sectional view of the non-orbiting scroll member illustrated in FIG. 4b at an intermediate coupling section;

FIG. 7 is a transverse cross-sectional view of a non-orbiting scroll member at an intermediate coupling section according to another embodiment of the present disclosure;

FIG. 8 is a perspective view, similar to FIG. 2, of a non-orbiting scroll member of a compression mechanism according to another embodiment of the present disclosure;

FIG. 9a is a cross-sectional view of a bulkhead according to an embodiment of the present disclosure, FIG. 9b is a partially cut-away perspective view of a bypass passage with the bulkhead of FIG. 9a attached to a connecting section, and FIG. 9c is a cross-sectional view of the bypass passage shown in FIG. 9 b; and

fig. 10a is a cross-sectional view of a choke plug according to another embodiment of the present disclosure, fig. 10b is a partially cut-away perspective view of a bypass passage with the choke plug of fig. 10a attached to a connecting section, and fig. 10c is a cross-sectional view of the bypass passage shown in fig. 10 b.

Detailed Description

The following description is merely exemplary in nature and is not intended to limit the present disclosure, application, or uses. It should be understood that throughout the drawings, corresponding reference numerals indicate like or corresponding parts and features. The present teachings are suitable for incorporation into many different types of vertical or horizontal scroll compressors, including hermetic machines, open drive machines, and non-hermetic machines. For purposes of example, the compressor 10 is shown as a low pressure side fully enclosed, vertical scroll compressor, i.e., wherein the motor is cooled by suction air in a sealed housing, as shown in the vertical cross-section of FIG. 1. However, the present teachings are equally applicable for incorporation in high side and horizontal compressors.

Example embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope to those skilled in the art. Numerous specific details are set forth such as examples of specific components, devices, and methods to provide a thorough understanding of embodiments of the present disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be embodied in many different forms and that neither should be construed to limit the scope of the disclosure. In some example embodiments, well-known methods, well-known device structures, and well-known technologies are not described in detail.

When an element or layer is referred to as being "on," "engaged to," "connected to" or "coupled to" another element or layer, it can be directly on, engaged, connected or coupled to the other element or layer or intervening elements or layers may be present. In contrast, when an element is referred to as being "directly on," or "directly engaged with," "directly connected to," or "directly coupled to" another element or layer, there are no intervening elements or layers present. Other words used to describe the relationship between elements should be interpreted in the same manner (e.g., "between …" versus "directly between …", "adjacent" versus "directly adjacent", etc.). As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.

Although the terms first, second, third, etc. may be used herein to describe various elements, components, regions, layers and/or sections, these elements, components, regions, layers and/or sections should not be limited by these terms. These terms may be only used to distinguish one element, component, region, layer or section from another region, layer or section. Terms such as "first," "second," and other numerical terms when used herein do not imply a sequence or order unless clearly indicated by the context. Thus, a first element, component, region, layer or section discussed below could be termed a second element, component, region, layer or section without departing from the teachings of the example embodiments.

Referring to fig. 1, a compressor 10 may include a housing, a refrigerant discharge fitting 14, a suction inlet fitting (not shown), a motor assembly, a bearing housing assembly, a compression mechanism, a retaining assembly, a seal assembly, and a valve assembly.

The housing may house the motor assembly, the bearing housing assembly, and the compression mechanism. The housing may include: a longitudinally extending housing 30 having a suction inlet (not shown); an end cap 34 having an exhaust outlet 36; a transversely extending partition 37; and a base 38. An end cap 34 may be secured to the upper end of the housing 30. The base 38 may be secured to the lower end of the housing 30. End cover 34 and diaphragm 37 may generally define a discharge pressure region, and diaphragm 37, housing 30 and base 38 may generally define a suction pressure region. The motor assembly, the bearing housing assembly and the compression mechanism are disposed in the suction pressure region. The diaphragm 37 includes an orifice 39, the orifice 39 providing communication between the compression mechanism and the discharge pressure region. The discharge pressure region may generally form a discharge muffler of the compressor 10. The refrigerant discharge fitting 14 may be attached to the housing at a discharge outlet 36 in the end cap 34. A suction inlet fitting may be attached to the housing 30 at the suction inlet. Although illustrated as including a discharge pressure zone, it should be understood that the present disclosure is not limited to compressors having a discharge pressure zone, but is equally applicable to inline configurations.

The motor assembly may generally include a stator 44, a rotor 46, and a drive shaft 48. The stator 44 may be press fit into the housing 30 and drive the rotor 46 to rotate through electromagnetic interaction with the rotor 46. The rotor 46 may be press fit onto the drive shaft 48. The drive shaft 48 is rotatably driven by the rotor 46 and is supported by a bearing housing assembly. A lubrication passage 50 is formed in the drive shaft 48 to supply lubrication from an oil sump formed at the base 38 to the upper bearing block assembly and the compression mechanism to provide lubrication. Drive shaft 48 may include an eccentric crank pin 52 having a flat on eccentric crank pin 52 for drivingly engaging the compression mechanism. The bearing housing assembly may include a lower bearing housing 56 and a main bearing housing 54 secured within the housing 30.

The compression mechanism may be driven by a motor assembly and may generally include an orbiting scroll member 60 and a non-orbiting scroll member 62. Orbiting scroll member 60 may include an end plate 64 and orbiting scroll blade 66 extending vertically upward from an upper surface of end plate 64. Non-orbiting scroll member 62 may include an end plate 74 and non-orbiting scroll blades 78 extending vertically downward from a lower surface of end plate 74. Non-orbiting scroll blade 78 may mesh with orbiting scroll blade 66, thereby forming a series of compression pockets. The volumes of these compression pockets vary throughout the compression cycle of the compression mechanism and may include an outermost suction pocket, several intermediate pockets, and a centrally located discharge pocket in the radial direction.

Referring to FIG. 2, non-orbiting scroll member 62 may include a first annular wall 80 on the opposite side of end plate 74 from the side on which non-orbiting scroll blade 78 is located. The first annular wall 80 surrounds a generally circular first region 84 within which the discharge port 88 and the bypass port 90 may be disposed. The exhaust port 88 may communicate with the exhaust cavity via an exhaust passage (exhaust port) 89, and the bypass port 90 may communicate with the intermediate cavity via a bypass passage 91. The first annular wall 80 defines an exhaust passage 20 radially inwardly thereof, the exhaust passage 20 selectively communicating with the exhaust pocket via an exhaust port 88 and an exhaust passage 89 and with the intermediate pocket via a bypass port 90 and a bypass passage 91.

In the embodiment shown in fig. 2, the bypass port 90 is shown as including three first and three

second bypass ports

90a, 90b formed generally symmetrically with respect to the central discharge port 88 to ensure that the compressor is switched between the low and high compression ratios stably and efficiently. The first bypass port 90a communicates with one intermediate cavity via a first bypass passage 91a and the second bypass port 90b communicates with another intermediate cavity on the opposite side via a second bypass passage 91b, each of which may correspond to one of the bypass passages, see fig. 5.

Non-orbiting scroll member 62 may also be provided with a second annular wall 82 radially outward of first annular wall 80. A generally annular second region 86 is enclosed between the first and second

annular walls

80, 82. A backpressure chamber 93 may be disposed in the second region 86 radially between the first and second

annular walls

80, 82, and the backpressure chamber 93 may communicate with one of the intermediate pockets of the compression mechanism via a backpressure passage (not shown) and establish a backpressure in the backpressure chamber 93. As such, non-orbiting scroll member 62 and orbiting scroll member 60 are maintained in abutment with one another during compression of the working fluid by the compression mechanism, while providing axial flexibility of the scroll members in cooperation with the retaining assembly, thereby ensuring safe and reliable operation of the compressor.

The retention assembly may generally include a sleeve 18 extending through the non-orbiting scroll member 62 and a fastener 16. Fasteners 16 may be secured to main bearing housing 54. The non-orbiting scroll member 62 may be fixed from rotation relative to the main bearing housing 54 by a retaining assembly that allows limited axial displacement of the non-orbiting scroll member 62 based on the back pressure of the back pressure chamber 93.

A sealing assembly, such as a floating seal assembly disposed in the back pressure chamber 93, is used in sealing engagement with the first and second

annular walls

80, 82 and the partition 37 to isolate the back pressure chamber 93 from the low and high pressure regions of the compressor 10.

The valve assembly may include a bypass valve 13 for controlling the opening and closing of the bypass port 90, the bypass valve 13 being a one-way valve. An exploded view of the bypass valve 13 is shown in fig. 2. As shown in fig. 2, the bypass valve 13 may include a valve plate 130, a valve member 132, a valve stop 133, and a biasing member 134. Valve plate 130 may be positioned above bypass port 90 such that discharge port 88 and bypass port 90 are exposed through an aperture in valve plate 130. The valve stop 133 may be secured to the valve plate 130 by fasteners such as bolts or pins, while the valve member 132 may be positioned and axially retained between the valve stop 133 and the valve plate 130. The valve member 132 is displaceable between open and closed positions. Biasing member 134 may bias valve plate 130, valve member 132, and valve stop 133 toward end plate 74 of orbiting scroll member 62 to hold them together. The biasing member 134 may take a variety of forms including, but not limited to, a helical spring, a crescent washer spring, or a wave washer spring.

In accordance with the arrangement of the bypass ports 90 on both sides, the valve member 132 may include a U-shaped body 136, with the annular body 136 defining an aperture 138. The annular body 136 may be radially aligned with the first and

second bypass ports

90a, 90b, and the orifice 138 may be radially aligned with the drain port 88. When in the closed position, the annular body 136 may sealingly engage the top surface of the valve plate 130 to seal the orifices of the valve plate 130 in communication with the first and

second bypass ports

90a, 90b to disconnect the

bypass ports

90a, 90b from the exhaust passage 20. At this time, the discharge port 88 may communicate with the exhaust passage 20 through a corresponding orifice in the valve plate 130 and an orifice 138 in the valve member 132. When in the open position, the annular body 136 of the valve member 132 may be biased axially upward against the valve stop 133, providing communication between the first and

second bypass ports

90a, 90b and the exhaust passage 20. At this point, discharge port 88 and bypass port 90 may both discharge compressed working fluid. The U-shaped configuration of the valve member 132 helps reduce the number of parts, but the present disclosure is not limited thereto, and the bypass valve 13 for sealing the first and

second bypass ports

90a and 90b, respectively, may be separately provided. It will be appreciated that different numbers and positions of bypass valves and bypass passages may be provided to selectively communicate intermediate pockets at different pressures. The bypass valve 13 is able to open unidirectionally upwards when the pressure in the corresponding intermediate cavity is greater than the pressure above the bypass valve 13 (the pressure in the exhaust passage 20). And when the pressure above the bypass valve 13 is greater than the pressure in the communicating intermediate cavity, the bypass valve 13 closes.

The valve assembly may further include a check valve provided at the orifice 39 of the diaphragm 37 as a main valve (not shown in the drawings) to set the discharge pressure of the discharge passage 20, and thus the discharge port 88 and the bypass port 90, to a system pressure outside the main valve (i.e., a condenser inlet pressure of a system in which the compressor 1 is provided). The highest pressure of the exhaust channel 20 is thus determined by the system pressure outside the main valve.

When compressor 10 is capable of providing a large volume or pressure ratio (i.e., a large discharge pressure), but the system requires a small volume or pressure ratio (i.e., a small system pressure), if the compression mechanism fully compresses the working fluid and discharges it at discharge port 88, the working fluid will be over-compressed and then partially expanded, resulting in some loss of efficiency. However, in the case of the bypass passage 91, when the working fluid is compressed halfway, the pressure in the corresponding intermediate cavity at one or more bypass valves 13 may already reach the discharge requirement, i.e. the system pressure, at which point the corresponding bypass valve 13 and the main valve may both be opened and the working fluid may be discharged in advance without excessive compression. On the other hand, when the compressor 10 is capable of providing a relatively small volume or pressure ratio, and the system requires a relatively large volume or pressure ratio, the pressure of the corresponding intermediate cavity may be less than the system pressure, failing to open the bypass valve 13. At this point, only the exhaust port 88 is open and pressure can build up in the exhaust passage 20 and cause the main valve to open upward above the system pressure above the main valve. In this way, the compression mechanism provides the system with working fluid at a pressure equal to or higher than the pressure of the discharge pocket in an adaptive manner.

Since the pressure in the compression pockets decreases toward the outer side, the bypass passage is provided as far outside as possible to achieve a large variable volume ratio range. However, considering that the bypass port 90 can be disposed only in the first region 84 surrounded by the first annular wall 80 together with the discharge port 88 and that a space for disposing the bypass valve 13 needs to be left, the disposition range of the bypass port 90 in the first region 84 is greatly limited, and further, the straight-up and straight-down bypass passage cannot be disposed further outside, resulting in a very limited design capacity of the volume ratio adjustment and a very limited degree of freedom in design of the bypass valve itself.

To this end, according to an embodiment of the present disclosure, the bypass passage may be provided to include an upper section and a lower section offset from each other in a radial direction, so that a radial position of the bypass passage in communication with the compression pocket can be adjusted within a range of less than ± d with respect to a radial position of the bypass port, where d is a diameter of the bypass passage.

This embodiment is described in detail below with reference to fig. 3a and 3b, where fig. 3a is a perspective view showing the configuration of a set (e.g., three) of bypass passages 91' including upper and lower sections offset from each other in the radial direction, fig. 3b is a schematic longitudinal cross-sectional view of a non-orbiting scroll member to which the bypass passages shown in fig. 3a are applied, and only one of the bypass passages is visible in the cross-sectional view of fig. 3 b. For clarity, in fig. 3a, other components are hidden from view, except for the bypass passage 91'. Bypass passage 91' extends generally perpendicular to end plate 74 of non-orbiting scroll member 62. As can be seen in the figure, each bypass passage 91 ' comprises an upper section 95 ' leading to the exhaust channel 20 and a lower section 97 ' leading to the intermediate cavity. Working fluid flows from the intermediate pocket into the lower section 97 ', via the junction of the lower section 97' and the upper section 95 ', into the upper section 95' along the arrows in fig. 3a, and finally into the exhaust channel 20 via the bypass port 90. The lower section 97 'is offset outboard in the radial direction relative to the upper section 95' to enable the bypass passage 91 'to communicate as far as possible with the outboard intermediate compression pocket, thereby widening the compressor's volume ratio range downwardly. However, as mentioned above, the communication position can only be adjusted in the radial direction, typically in the order of a few millimeters.

The configuration of the bypass passage 91 according to another embodiment of the present disclosure is described below with reference to fig. 4a-4b, 5, and 6. Similar to fig. 3a, other components are omitted from fig. 4a, showing a perspective view of only one set (three) of bypass passages 91 of this embodiment, fig. 4b is a schematic longitudinal cross-sectional view of the non-orbiting scroll member 62 to which the bypass passages 91 shown in fig. 4a are applied, fig. 5 is a partial cross-sectional perspective view of the non-orbiting scroll member 62 shown in fig. 4b, and fig. 6 is a transverse cross-sectional view of the non-orbiting scroll member 62 shown in fig. 4b at an intermediate connection section 99. As shown, unlike bypass passage 91' of the previous embodiment, bypass passage 91 includes an upper section 95 that extends to exhaust passage 20 generally perpendicular (i.e., may be either completely perpendicular or slightly inclined) to end plate 74 of non-orbiting scroll member 62, a lower section 97 that extends to intermediate pocket generally perpendicular to end plate 74, and a transverse connecting section 99 that extends generally parallel to the plane of end plate 74 and connects upper section 95 and lower section 97. In the cross-sectional view of fig. 4b, only the lower section 97 of one of the bypass passages is visible. Working fluid flows from the intermediate pocket into the lower section 97, via the intermediate connecting section 99 into the upper section 95, and finally into the exhaust channel 20 via the exhaust port 88, as indicated by the arrows in fig. 4 a. Thus, the location of the aperture of the lower section 97 is no longer limited by the location of the aperture of the upper section 95, but rather can be disposed radially outwardly of the first region 84 away from the vertical extent of the first region 84 as required to communicate with the more outwardly intermediate pockets of lower pressure of the scroll mechanism, thereby allowing the range of variation of the variable volume ratio of the compressor 10 to be widened downwardly in a desired manner, improving the overall efficiency of the system. In addition, since the size of the intermediate connection section 99 may be larger than the size of the upper and

lower sections

95 and 97 and the upper and

lower sections

95 and 97 may not communicate in a staggered manner but may communicate completely with the connection section 99, the intermediate connection section 99 communicates with the upper and

lower sections

95 and 97 more smoothly and exhausts gas, and this allows the size of the lower section 97 to be increased, thereby further improving the bypass efficiency and the variable volume ratio efficiency of the compressor 10 and facilitating noise reduction. Further, in addition to the greater degree of freedom in design of the opening position of the lower section 97, the opening position of the upper section 95 can be arbitrarily adjusted within the first region 84, thereby making it possible to make the design of the bypass valve 13 more convenient and versatile.

In the embodiment shown in fig. 4a, since the three bypass passages 91 are arranged along the profile (curve) of the scroll blade and are all disposed radially outside the first region 84, the size of the transverse connecting section 99 cannot be set too large in view of the strength of the non-orbiting scroll member 62, and therefore one transverse connecting section 99 often fails to meet the design requirements of the opening position of the upper section 95, and for this purpose a combination of two cross-communicating connecting sections is used, one of which protrudes into the first region 84 at a suitable position for disposing the upper section 95. As shown in fig. 5, in the case where there are two sets of bypass passages, i.e., one set of three first bypass passages 91a and one set of three second bypass passages 91b, four lateral connecting sections 99a1, 99a2 and 99b1, 99b2 may be opened as needed. Also, in each set of bypass passages, there may be three lower sections or only two of them defining the orientation of one connection section, i.e. in direct communication with one connection section. Accordingly, the further connection section may not be in direct communication with the lower sections or only with one of the lower sections, and therefore its orientation may be adjusted to a suitable position for placing the upper section thereon as required. As shown in fig. 6, of the two connecting sections 99a1 and 99b1 of the two sets of

bypass passages

91a and 91b for providing the

upper sections

95a and 95b, one connecting section 99b1 directly communicates with the middle lower section and one connecting section 99a1 directly communicates with the inside lower section.

It should be noted that the number of connecting sections provided is related to the number and location of the bypass passages, and more or fewer intermediate connecting sections may be provided as desired. For example, in the case where one bypass passage is provided on each of both sides, the orientation of the connecting sections can be adjusted as desired, and therefore only one connecting section may be provided on each side instead of two connecting sections that are in cross communication. Conversely, in the case where the number of bypass passages per group exceeds three and are arranged discretely, even more connecting sections may be required for realizing these bypass passages. In addition, as described above, since the hole positions of the upper sections can be arbitrarily adjusted by appropriate setting of the connecting sections, it is allowed to guide the exhaust gas of the lower sections of the two sets of bypass passages provided on both sides to one position by means of the connecting sections for discharge, that is, it is allowed to provide only one upper section and one bypass port for bypassing the intermediate cavities on both sides. This arrangement obviously saves the design space of the first region 84.

For example, with reference to the embodiment shown in fig. 7, the two sets of

bypass passages

91a, 91a and 91b, 91b on both sides are both two in number and share one upper section 95 and one bypass port 90 for both sets of

bypass passages

91a, 91a and 91b, 91b on both sides, for which purpose the two sets of bypass passages are respectively arranged such that a connecting section 99a communicating with both

lower sections

97a, 97a and a connecting section 99b communicating with both

lower sections

97b, 97b can be oriented to extend towards the common upper section 95 and communicate to this same upper section 95. Although in the embodiment shown in fig. 7, the number of each group of bypass passages is two and one connecting section is employed, the present disclosure is not limited thereto, and the number of each group of bypass passages may be one or more than two and more than one connecting section may be employed as long as the connecting sections that directly communicate with the upper sections are arranged to open to the common upper section.

In such a case where only one upper section 95 and one bypass port 90 are provided, as shown in fig. 8, instead of providing a total valve at the orifice 39 of the partition 37, a one-way discharge valve (HVE) for controlling the discharge pressure may be provided at the discharge port 88, and the discharge valve may be provided separately from the single bypass valve or provided integrally as shown in fig. 8. In the embodiment shown in fig. 8, the function of the bypass valve and the discharge valve can be realized at the same time by the specially designed valve 113, which simplifies the structure, and further improves the efficiency of the scroll compressor and thus the system, not only improving the efficiency in the over-compression state, but also improving the efficiency in the under-compression state. Similar to the bypass valve 13 shown in FIG. 2, the check valve 113 in FIG. 8 also includes a valve plate 130, a valve member 132, a valve stop 133, and a biasing member 134. In accordance with the arrangement of the discharge and

bypass ports

88, 90, the sheet-like body of the valve member 132 may include two portions that are aligned in radial position with the discharge and

bypass ports

88, 90, respectively, and serve to cover the orifices in the valve plate 130 corresponding to the discharge and

bypass ports

88, 90, with the valve member 132 itself not including the orifices 138 (see fig. 2).

When under-compressed, both the bypass valve and the discharge valve may be closed, and the scroll compressor continues to compress until the discharge pocket pressure is higher than the system pressure above the discharge valve causing the discharge valve to open; when in an over-compression condition, the pressure in the intermediate cavity communicating through the bypass passage is already above the system pressure above the bypass valve, both the bypass valve and the discharge valve may be open, and the compressor may be operated at a low volume ratio.

These check valves described above only allow one-way outflow of the working fluid from the compression pockets, thereby substantially preventing backflow of the compressed gas or preventing the compressor from reversing direction after shutdown. And these may be any suitable type of one-way valve, such as a valve flap, spring-loaded one-way valve, etc.

It is understood that the design concept of the bypass passage of the present invention is not limited to the configuration of the bypass passage shown in the drawings, and all modifications of designing the bypass passage such that the position of the bypass port deviates in the radial direction from the position of the bypass passage communicating to the intermediate cavity fall within the scope of the present invention. For example, instead of a straight-up and straight-down one-section bypass passage, the bypass passage may be inclined or curved to extend in comparison with the vertical direction or the horizontal direction. Similarly, the bypass passage of multiple segments in the embodiment shown in the figures may also be configured to include upper, lower and/or connecting segments that extend at an angle that is inclined compared to the vertical or horizontal direction. Therefore, "longitudinal" or "lateral" in this document cannot be construed as a vertical direction or a horizontal direction in a strict sense unless explicitly stated otherwise.

In addition, although in the above-described embodiment, the two sets of bypass passages are shown to be disposed substantially symmetrically with respect to the longitudinal axis of the end plate of the non-orbiting scroll member, the present invention is not limited thereto, and the two sets of bypass passages may be disposed accordingly according to whether the design of the compression mechanism is symmetrical or not without affecting the normal operation of the compression mechanism, and the configuration and the number of the two sets of bypass passages may be different from each other.

It should be noted that, since the connection section is provided inside the solid end plate of the non-orbiting scroll member, the lateral connection section is formed by punching from the circumferential side surface of the end plate and extending up to the end portion communicating with the upper section, subject to the limitation of the machining method. This means that the actual length of the intermediate connecting section exceeds its required length. The bypass passage is longer due to the longer connecting section connecting the lower section and the upper section of the bypass passage. After the system pressure rises such that the bypass valve closes, the long bypass path may cause the clearance volume of the scroll member to be excessive, resulting in a decrease in compressor efficiency. According to one embodiment of the disclosure, a method of matching a specially designed threaded hole with a plug is used for preventing a compression working medium from entering an invalid volume (namely, an invalid VVR volume section) from an effective volume (namely, an effective VVR volume section) of a bypass passage, so that the clearance volume can be greatly reduced, the efficiency of a compression mechanism is improved, and meanwhile, the influence of a transverse process hole on the strength of a scroll component can be reduced.

Two embodiments of a bypass passage including a bulkhead mounted connecting section according to the present disclosure are described below with reference to fig. 9a-9c and 10a-10 c. Fig. 9a is a cross-sectional view of a plug 103 according to an embodiment of the present disclosure, fig. 9b is a partially cut-away perspective view of

bypass passages

91a and 91b to which the plug 103 of fig. 9a is attached, and fig. 9c is a cross-sectional view of the

bypass passages

91a and 91b of fig. 9 b. Fig. 10a is a cross-sectional view of a choke plug 203 according to another embodiment of the present disclosure, fig. 10b is a partially cut-away perspective view of

bypass passages

91a and 91b with the choke plug 203 of fig. 10a installed, and fig. 10c is a cross-sectional view of the

bypass passages

91a and 91b shown in fig. 10 b. Wherein components other than the bypass path are omitted from the figure for clarity.

In the embodiment shown in fig. 9a to 9c, the plug 103 has a short stud shape, and a tool engagement groove 105 is formed on one end surface of the plug 103, as shown in fig. 9 a. An internal thread is formed on the inside surface of the lateral process hole forming the

connection sections

99a and 99b, the internal thread extending from the opening position of the lateral process hole on the circumferential side surface of the end plate up to the communication position of the lateral process hole communicating with the lower section, that is, over the entire longitudinal length of the dead volume of the lateral process hole. After the

bypass passageways

91a and 91b are completely perforated and the dead volume is formed as a threaded hole, the dead volume is isolated from the active volume by engaging a tool, such as a screwdriver, with the tool engagement recess 105 on the plug 103 and screwing the plug 103 into the threaded hole and securing the dead volume at the location where the dead volume abuts the active volume. Thus, compressed working fluid entering the connection section from the lower section is intercepted by the plug 103 and cannot enter the dead volume, but can only enter the upper section along the active connection section (the active volume of the present disclosure) and exit the bypass port.

In another embodiment shown in fig. 10a to 10c, the stopper 203 has a long stepped cylindrical shape and comprises a first cylindrical portion 206 and a second cylindrical portion 207, the length of the first cylindrical portion 206 being much smaller than the length of the second cylindrical portion 207. As shown in fig. 10a, the first cylindrical portion 206 is formed in the shape of a stud with an external thread for engaging an internal thread formed in the lateral tooling hole, similar to the plug 103 shown in fig. 9a, and the first cylindrical portion 206 is formed with a tool engaging recess 205 on an end surface opposite to an end surface to which the second cylindrical portion 207 is connected, for engaging a tool such as a screwdriver. The diameter of the second cylindrical portion 207 is slightly smaller than the first cylindrical portion 206, more precisely slightly smaller than the inner diameter of the connecting section. Unlike the first cylindrical portion 206, the outer peripheral surface of the second cylindrical portion 207 is smooth and not threaded. Accordingly, the lateral tooling holes for forming the

connection sections

99a and 99b are formed with internal threads having a length corresponding to that of the first cylindrical portion 206 only at the positions of the holes located on the circumferential side surface of the end plate. When the plug 203 is installed, the second cylindrical portion 207 is inserted into the transverse bore, and finally the first cylindrical portion 206 is screwed into the transverse bore by means of a tool into engagement with the internal thread at the location of the bore and fixed. In such an embodiment, the length of the second cylindrical portion 207 may be flexibly determined based on the difference between the length of the dead volume and the length of the first cylindrical portion 206 to minimize the residual clearance volume.

It can be seen that the purpose of substantially eliminating the clearance volume and thus improving the efficiency of the compression mechanism can be achieved in both the former embodiment in which the short plug is matched with the long threaded hole and the latter embodiment in which the short threaded hole is matched with the long plug, and the two embodiments can be flexibly selected according to the situation in practice. In addition, both embodiments, particularly those employing long plugs, are particularly advantageous for increasing the strength of the non-orbiting scroll member.

Although various embodiments and modifications of the present disclosure have been specifically described above, it will be understood by those skilled in the art that the present disclosure is not limited to the specific embodiments and modifications described above but may include other various possible combinations and combinations. Other modifications and variations may be effected by one skilled in the art without departing from the spirit and scope of the disclosure. All such variations and modifications are intended to fall within the scope of the present disclosure. Moreover, all the components described herein may be replaced by other technically equivalent components.

Claims

1. A scroll compressor, comprising:

a first scroll member including a first end plate and a first scroll blade extending from the first end plate;

a second scroll member including a second end plate and a second scroll blade extending from the second end plate, the second scroll blade meshing with the first scroll blade to form a series of compression pockets including a suction pocket, a plurality of intermediate pockets, and a discharge pocket,

it is characterized in that the preparation method is characterized in that,

the first end plate includes a bypass passage extending therethrough, one end of the bypass passage communicating with an exhaust passage via a bypass port and the other end communicating with the intermediate cavity, the bypass port being located at a position offset in a radial direction from a position at which the bypass passage communicates to the intermediate cavity.

2. The scroll compressor of claim 1, wherein the bypass passage includes a first section and a second section in communication with each other, the first section leading to the intermediate cavity and the second section leading to the discharge passage.

3. The scroll compressor of claim 2, wherein the bypass passage further comprises a laterally extending connecting section connecting the first section and the second section.

4. The scroll compressor of claim 3,

the first end plate including a first annular wall surrounding a first region on a side opposite the first scroll blade, the first annular wall defining the exhaust passage,

the first end plate further includes a discharge passage extending through the first end plate, one end of the discharge passage communicating with the exhaust gas channel via a discharge port and the other end communicating with the discharge cavity, and

the discharge port and the bypass port are both disposed within the first region.

5. The scroll compressor of claim 1, wherein a bypass valve is provided at the bypass port, the bypass valve being a one-way valve.

6. The scroll compressor of claim 4, wherein the bypass passages comprise a first set of bypass passages comprising one or more first bypass passages and a second set of bypass passages comprising one or more second bypass passages.

7. The scroll compressor of claim 6,

in the first group of bypass passages, the first section is one or more, the second section is one or more, the first section and the second section are directly communicated through one connecting section, and

in the second group of bypass passages, the first section is one or more, the second section is one or more, and the first section and the second section are directly communicated through one connecting section.

8. The scroll compressor of claim 6,

the first set of bypass passages includes a plurality of first bypass passages in which the connection section includes a first connection section directly communicating with part or all of the first sections and a second connection section directly communicating with the rest of the first sections, the first connection section, and the second section, and

the second set of bypass passages includes a plurality of second bypass passages, and among the plurality of second bypass passages, the connection section includes a first connection section and a second connection section, the first connection section directly communicates with part or all of the first sections, and the second connection section directly communicates with the remaining first sections, the first connection sections, and the second sections.

9. The scroll compressor of claim 7 or 8, wherein the one or more first bypass passages comprise a respective one or more of the second sections, and the one or more second bypass passages comprise a respective one or more of the second sections.

10. The scroll compressor of claim 7 or 8, wherein the one or more first bypass passages share a second section and the one or more second bypass passages share a second section.

11. The scroll compressor of claim 10, wherein the one or more first bypass passages and the one or more second bypass passages share one of the second sections and one of the bypass ports.

12. The scroll compressor of claim 11, wherein a discharge valve is provided at the discharge port and a bypass valve is provided at the bypass port, the discharge valve and the bypass valve being one-way valves.

13. The scroll compressor of claim 12, wherein the bypass valve is provided separately from the discharge valve or the bypass valve and the discharge valve are provided as an integrated valve in which at least one of a valve plate, a valve member, a valve stop and a biasing member is a common member.

14. The scroll compressor of any one of claims 4, 6, 7 and 8, wherein the first section is disposed radially outward of the first region in a radial direction away from the second section.

15. The scroll compressor of any one of claims 3, 4, 6, 7 and 8, wherein the connecting section includes an active volume section and an inactive volume section, the inactive volume section extending from an open position of the connecting section to a communicating position in communication with the other sections, the scroll compressor further comprising a choke plug for eliminating the inactive volume section.

16. The scroll compressor of claim 15, wherein one end face of the choke plug includes a tool engagement recess for engagement by a tool to insert the choke plug into the dead volume section.

17. The scroll compressor of claim 15, wherein the connecting section includes internal threads throughout the length of the dead volume section, the plug is in the form of an externally threaded stud, the length of the plug is less than the length of the dead volume section, and the dead volume section can be isolated from the active volume section by threading the plug into the dead volume section and securing the plug at a location where the dead volume section abuts the active volume section.

18. The scroll compressor of claim 15, wherein the connecting section is internally threaded only at the location of the opening thereof, the bulkhead is in the shape of a stepped cylinder and includes a first cylindrical portion and a second cylindrical portion having a diameter slightly smaller than the first cylindrical portion, the first cylindrical portion having an external thread formed on an outer peripheral surface thereof for engagement with the internal thread, the second cylindrical portion having a length set to fill the dead volume section.

19. The scroll compressor of any one of claims 4, 6, 7 and 8, wherein the first end plate further comprises a second annular wall radially outward of the first annular wall, the first and second annular walls defining a back pressure chamber therebetween, and the back pressure chamber communicates with one of the intermediate pockets via a back pressure passage extending through the first end plate, the intermediate pocket communicating with the back pressure passage being different from the intermediate pocket communicating with the bypass passage.

20. The scroll compressor of any one of claims 1 to 8, wherein the discharge passage communicates with a discharge pressure region of the scroll compressor via a one-way valve.