CN111794960B

CN111794960B - Scroll compressor having a rotor with a rotor shaft having a rotor shaft with a

Info

Publication number: CN111794960B
Application number: CN201910281279.8A
Authority: CN
Inventors: 刘轩; 金培
Original assignee: Gulun Environmental Technology Suzhou Co ltd
Current assignee: Gulun Environmental Technology Suzhou Co ltd
Priority date: 2019-04-09
Filing date: 2019-04-09
Publication date: 2024-07-12
Anticipated expiration: 2039-04-09
Also published as: CN111794960A

Abstract

The present invention provides a scroll compressor comprising a compression mechanism adapted to compress a working fluid and comprising: the fixed vortex comprises a fixed vortex end plate and a fixed vortex scroll; and an orbiting scroll including an orbiting scroll end plate and an orbiting scroll wrap, wherein a low pressure region having a suction pressure and the remaining high pressure region are formed between the orbiting scroll wrap and the orbiting scroll wrap, wherein the scroll compressor further includes at least one fluid passage introducing a high temperature fluid having a temperature higher than that in the low pressure region into the low pressure region and a check valve controlling opening and closing of the fluid passage. The scroll compressor can solve the problem of fluid flash evaporation, thereby avoiding overlarge local temperature difference, eliminating temperature fatigue stress in the scroll wrap, greatly prolonging the service life, and has simple structure, easy processing and manufacturing and higher cost benefit.

Description

Scroll compressor having a rotor with a rotor shaft having a rotor shaft with a

Technical Field

The present invention relates to a scroll compressor, and more particularly, to a scroll compressor which improves a local temperature difference of a scroll wrap in a compression mechanism.

Background

This section provides background information related to the present invention, which does not necessarily constitute prior art.

Scroll compressors may be used in, for example, refrigeration systems, air conditioning systems, and heat pump systems. The scroll compressor includes a compression mechanism for compressing a working fluid (e.g., refrigerant), the compression mechanism including an orbiting scroll and a non-orbiting scroll, the non-orbiting scroll including a non-orbiting scroll end plate and a non-orbiting scroll wrap extending from a side of the non-orbiting scroll end plate, the orbiting scroll including an orbiting scroll end plate and an orbiting scroll wrap extending from the orbiting scroll end plate, wherein the orbiting scroll remains stably engaged with the non-orbiting scroll, and upon operation of the scroll compressor, the orbiting scroll makes an orbiting relative movement with respect to the non-orbiting scroll such that the orbiting scroll wrap and the non-orbiting scroll wrap remain in dynamic engagement with each other to form a low pressure region having a suction pressure and a high pressure region having a pressure higher than the suction pressure between the orbiting scroll wrap and the non-orbiting scroll wrap. When the scroll compressor is operated, fluid to be compressed enters the compression mechanism through the low pressure region and is compressed in the high pressure region to form high temperature and high pressure fluid, which is finally discharged to the outside of the compression mechanism through the discharge port on the fixed scroll end plate.

Flash phenomena often occur when scroll compressors are operated, particularly at high pressure ratio conditions. The liquid refrigerant is mixed in the gaseous refrigerant and therewith enters the suction chamber of the compression mechanism, where it flashes and thus absorbs rapidly the temperature in the suction chamber. Therefore, the temperature in the suction chamber is suddenly reduced, so that the temperature difference between two sides of the scroll wrap is increased, and the scroll wrap is cracked or even fails.

Accordingly, there is a need to provide a scroll compressor that can solve or alleviate the problem of the scroll wrap in the compression mechanism being destroyed by flash evaporation.

Disclosure of Invention

The accompanying drawings are included to provide a general overview of the invention and are not intended to provide a complete disclosure of the full scope of the invention or all-character thereof.

The present invention aims to improve one or more of the technical problems mentioned above. In general, the inventors have made extensive studies on the problem of the above-described working fluid flash evaporation, and developed a scroll compressor capable of effectively avoiding or significantly reducing the occurrence of fluid flash evaporation to substantially eliminate the problem of excessive local temperature difference in a compression mechanism, as described below, thereby avoiding damage to the compression mechanism by temperature fatigue stress in the scroll wrap.

According to one aspect of the present invention, there is provided a scroll compressor comprising a compression mechanism adapted to compress a working fluid and comprising:

A non-orbiting scroll including a non-orbiting scroll end plate and a non-orbiting scroll wrap extending from a first side of the non-orbiting scroll end plate; and

An orbiting scroll including an orbiting scroll end plate and an orbiting scroll wrap extending from a first side of the orbiting scroll end plate,

Wherein a low pressure region having a suction pressure and a remaining high pressure region are formed between the fixed scroll wrap and the movable scroll wrap,

Wherein the scroll compressor further comprises at least one fluid passage configured to introduce a high temperature fluid having a temperature higher than that in the low pressure region into the low pressure region and a check valve disposed to control opening and closing of the fluid passage.

By providing the above fluid passage to supply high temperature fluid in the low pressure region where fluid flash evaporation is likely to occur, the heat absorbed by the fluid flash evaporation can be compensated for, thereby reducing or avoiding local temperature drop, and thereby avoiding fatigue stress caused by local temperature difference.

According to one aspect of the present invention, the check valve is a solenoid valve or a mechanical valve and is provided in the fluid passage, the check valve being configured to: opening the fluid passage to allow the high-temperature fluid to enter the low-pressure region when a difference between the pressure of the high-temperature fluid and the suction pressure in the low-pressure region is equal to or greater than a predetermined differential pressure; and closing the fluid passage to prevent the high temperature fluid from entering the low pressure region when a difference between the pressure of the high temperature fluid and the suction pressure in the low pressure region is less than the predetermined pressure difference.

The timing at which the check valve is opened and the opening time period can be appropriately defined according to the actual application by setting the predetermined differential pressure, thereby controlling the supply amount of the high-temperature fluid.

Depending on the practical application, various high-temperature fluid sources as described below may be employed to supply the high-temperature fluid, and appropriate fluid passages may be provided depending on the employed high-temperature fluid source, as long as the high-temperature fluid can be surely delivered into the low-pressure region.

According to one aspect of the invention, the fluid passageway introduces the high temperature fluid at the high pressure region to the low pressure region.

According to one aspect of the invention, the fluid passage introduces the high temperature fluid in the back pressure chamber to the low pressure region.

According to one aspect of the invention, the back pressure chamber is disposed on a second side of the non-orbiting scroll end plate opposite the first side of the non-orbiting scroll end plate, and the fluid passage is configured as a through hole disposed in the non-orbiting scroll end plate extending directly from the back pressure chamber to the low pressure region.

According to one aspect of the invention, the fluid passageway is configured to introduce the high temperature fluid outside the compression mechanism, inside the housing of the scroll compressor, to the low pressure region.

According to one aspect of the invention, the fluid passageway is configured to introduce the high temperature fluid in a fluid line of a system including the scroll compressor to the low pressure region.

According to one aspect of the invention, the fluid passage includes a low temperature orifice opening toward the low pressure region, the low temperature orifice being proximate to the air inlet of the compression mechanism.

According to one aspect of the invention, the cryogenic orifice is disposed in the non-orbiting scroll end plate.

According to one aspect of the invention, the one-way valve comprises:

An end cap defining an aperture for passage of a fluid;

A blocking member; and

The spring is arranged on the inner side of the cylinder,

Wherein the spring urges the barrier against the orifice to form a gas-tight seal when the difference between the pressure of the high temperature fluid and the suction pressure in the low pressure region is less than the predetermined pressure differential, and the barrier separates from the orifice when the difference between the pressure of the high temperature fluid and the suction pressure in the low pressure region is greater than the predetermined pressure differential.

According to one aspect of the invention, the one-way valve comprises:

a valve cover defining an aperture for passage of fluid; and

A valve plate, one end of which is fixed relative to the valve cover,

Wherein the valve sheet covers the orifice to form an airtight seal when a difference between the pressure of the high temperature fluid and the suction pressure in the low pressure region is less than the predetermined pressure difference, and is elastically deformed to be separated from the orifice when a difference between the pressure of the high temperature fluid and the suction pressure in the low pressure region is greater than the predetermined pressure difference.

In summary, the scroll compressor according to the present invention provides at least the following advantages: the scroll compressor can solve the problem of fluid flash evaporation, thereby avoiding overlarge local temperature difference in a compression mechanism, further eliminating temperature fatigue stress in the scroll wrap, greatly prolonging the service life, and has simple structure, easy processing and manufacturing and higher cost benefit.

Drawings

The foregoing and additional features and characteristics of the present invention will become more apparent from the following detailed description, taken in conjunction with the accompanying drawings, which are merely exemplary and not necessarily drawn to scale. Like reference numerals are used to designate like parts throughout the accompanying drawings, in which:

FIG. 1 illustrates a longitudinal cross-sectional view of a scroll compressor according to the present invention;

FIG. 2a shows a cross-sectional view of a non-orbiting scroll provided with a fluid passageway in accordance with a first embodiment of the present invention;

FIG. 2b shows an enlarged partial view of the fluid pathway of FIG. 2a including a one-way valve;

FIG. 3 illustrates a schematic bottom view of a non-orbiting scroll according to a first embodiment of the invention;

FIG. 4a shows a cross-sectional view of a non-orbiting scroll provided with a fluid passageway in accordance with a second embodiment of the present invention;

FIG. 4b shows an enlarged partial view of the fluid pathway of FIG. 4a including a one-way valve;

FIG. 5 illustrates a check valve in a fluid path of a non-orbiting scroll in accordance with a third embodiment of the present invention;

FIG. 6a illustrates a partial cross-sectional view of a non-orbiting scroll provided with a fluid passageway in accordance with a fourth embodiment of the present invention; and

Fig. 6b shows an enlarged partial view of the fluid pathway of fig. 6a including a one-way valve.

List of reference marks

A scroll compressor 1; a housing 12; a cover 26; a base 28; baffle 19

A stator 14; a rotor 15; a hub 240; oil pool O

A low-pressure space A1; high-pressure space A2; a drive shaft 16; main bearing block 40

A compression mechanism CM; a fixed scroll 22; an orbiting scroll 24; fixed scroll end plate 221

A fixed scroll wrap S2; an orbiting scroll end plate 241; orbiting scroll S4

A fluid passage 13; low Wen Kongkou 130,130; a high temperature orifice 132; scroll end S0

A low pressure region DL; a high-pressure region DH; a one-way valve V; back pressure chamber B

End cap G, blocking member T, spring P, spacer K, orifice G0

Valve plate V1; valve gear V2; a valve cover V3; an orifice V0; a lower gap j; upper interval h

Detailed Description

Preferred embodiments of the present invention will now be described in detail with reference to fig. 1-6 b. The following description is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses.

For convenience of description, the scroll compressor as shown in fig. 1 is exemplarily shown as a low pressure side scroll compressor, i.e., a compression mechanism is located in a low pressure space, however, the scroll compressor according to the present invention is not limited to this type, and the present invention is also applicable to other suitable types of scroll compressors, such as a high pressure side scroll compressor, a compression mechanism is located in a high pressure space. This will be described in detail below.

Fig. 1 shows a longitudinal sectional view of a scroll compressor according to the present invention. First, the overall structure of the scroll compressor according to the present invention is schematically described with reference to fig. 1.

As shown in fig. 1, the scroll compressor 1 includes a generally cylindrical housing 12, an electric motor (including a stator 14 and a rotor 15), a drive shaft 16, a main bearing housing 40, and a compression mechanism CM adapted to compress a working fluid (e.g., refrigerant).

A cover 26 at the top of the housing 12 and a base 28 at the bottom of the housing 12 may be mounted to the housing 12, defining an interior volume of the scroll compressor 1. A lubricant such as lubricating oil may be stored in the oil sump O in the bottom of the housing 12 for lubricating various components of the scroll compressor 1 (e.g., the orbiting scroll 24, the non-orbiting scroll 22, the thrust plate, etc.).

The scroll compressor 1 further includes a partition 19 provided between the head cover 26 and the housing 12 to partition an inner space of the scroll compressor 1 into a high-pressure space A2 and a low-pressure space A1. The diaphragm 19 and the cover 26 form a high-pressure space A2 therebetween, and the diaphragm 19, the housing 12, and the base 28 form a low-pressure space A1 therebetween. An intake pipe 18 for introducing a low-pressure working fluid to be compressed is provided on the housing 12 at the low-pressure space A1, and an exhaust pipe 17 for discharging the compressed high-temperature high-pressure fluid to the outside of the scroll compressor 1 is provided in the high-pressure space A2. As described above, the embodiment shown in fig. 1 is exemplified by a low-pressure side scroll compressor, and therefore, as shown in fig. 1, the compression mechanism CM is located in the low-pressure space A1.

The compression mechanism CM includes an orbiting scroll 24 and a fixed scroll 22. The non-orbiting scroll 22 includes a non-orbiting scroll end plate 221 and a non-orbiting scroll wrap S2; the orbiting scroll 24 includes an orbiting scroll end plate 241, an orbiting scroll wrap S4 extending from a first side of the orbiting scroll end plate 241, and a hub 240 extending from a second side of the orbiting scroll end plate 241. The compression mechanism CM is defined with: an open suction chamber in fluid communication with the outside of the compression mechanism CM, the suction chamber having an air inlet in fluid communication with the low pressure space A1 within the housing 12 to introduce the working fluid to be compressed in the low pressure space A1 into the compression mechanism CM; a series of closed chambers (described in detail below) formed by the engagement of the fixed scroll wrap and the orbiting scroll wrap; and an exhaust port C located at the radial center of the non-orbiting scroll end plate 221, the exhaust port C being in fluid communication with the high pressure space A2 inside the housing 12 and exhausting the compressed high temperature and pressure fluid into the high pressure space A2.

In contrast, for the high-pressure side scroll compressor, the compression mechanism CM is located in the high-pressure space, and the compression mechanism CM likewise introduces the low-pressure working fluid from the low-pressure space and discharges the compressed high-temperature and high-pressure fluid to the high-pressure space, and therefore, the operation principle of the high-pressure side scroll compressor is substantially the same as that of the low-pressure side scroll compressor, and the difference is mainly that the space pressure where the compression mechanism CM is located is different, which will not be described again.

The electric motor comprises a stator 14 and a rotor 15. The rotor 15 is used to drive the drive shaft 16 to rotate the drive shaft 16 about its rotational axis relative to the housing 12. The drive shaft 16 may include an eccentric pin mounted to the first end (tip) of the drive shaft 16 or integrally formed with the first end of the drive shaft 16.

The drive shaft 16 may include a central hole formed at a second end (bottom end) of the drive shaft 16 and an eccentric hole (not shown) extending upward from the central hole to an end surface of the eccentric pin. The end (lower end) of the center hole may be immersed in the oil pool O at the bottom of the housing 12 of the scroll compressor 1 so that the lubricating oil can be delivered from the oil pool O, for example, by centrifugal force generated by the rotation of the drive shaft 16, and flow upward through the center hole and the eccentric hole and out from the end surface of the eccentric pin.

The lubricating oil flowing out of the end surface of the eccentric pin may flow into a lubricating oil supply region formed between the eccentric pin and the orbiting scroll 24 and between the main bearing housing 40 and the orbiting scroll 24, for example. The lubrication oil in this lubrication oil supply region may lubricate, for example, the rotary joint and sliding surfaces between the eccentric pin and the orbiting scroll 24 and between the main bearing housing 40 and the orbiting scroll 24, and the lubrication oil in the lubrication oil supply region may also be supplied to the compression mechanism CM.

The orbiting scroll 24 is axially supported by the main bearing housing 40 and is supported by the main bearing housing 40 to be capable of orbiting. The hub 240 of the orbiting scroll 24 may be rotatably coupled to an eccentric pin. Alternatively, the hub 240 may be rotatably coupled to the eccentric pin via a sleeve or bearing.

The non-orbiting scroll 22 is mounted to the main bearing housing 40, for example using mechanical fasteners. The orbiting scroll 24 is driven by an electric motor via a drive shaft 16 (specifically, an eccentric pin) so as to be capable of translational rotation with respect to the non-orbiting scroll 22 by means of an oldham ring-i.e., orbiting (i.e., the axis of the orbiting scroll 24 orbits with respect to the axis of the non-orbiting scroll 22, but both the orbiting scroll 24 and the non-orbiting scroll 22 do not themselves rotate about their respective axes). Thus, each chamber defined by the fixed scroll wrap S2 and the movable scroll wrap S4 changes from the open suction chamber to a series of closed chambers as follows during movement from the radially outer side to the radially inner side: the middle pressure compression chamber (pressure greater than suction pressure and less than discharge pressure) that becomes intermediate from the outer low pressure chamber becomes the high pressure compression chamber (having the highest pressure, i.e., equal to discharge pressure) at the center, and the volume of the chamber gradually becomes smaller from larger. In this way, the pressure of the fluid also gradually increases, so that the working fluid (e.g., refrigerant) in the chamber is compressed and finally discharged from the discharge port C located at the radial center of the non-orbiting scroll end plate 221 into the high pressure space A2 outside the compression mechanism, thereby achieving a working cycle of suction, compression, and discharge of the working fluid.

In each of the chambers described above, the open aspiration chamber has an aspiration pressure, and in the series of closed chambers formed there is a low pressure chamber having an aspiration pressure as follows: the low pressure chamber having a suction pressure is a closed low pressure chamber having a suction pressure adjoining the suction chamber, which is defined by the engagement of the movable scroll S4 with the fixed scroll S2 immediately after the working fluid to be compressed is introduced into the compression mechanism CM. For convenience of description herein, the overall area of the suction chamber and the closed instantaneous low pressure chamber having suction pressure is referred to as a "low pressure area" having suction pressure, and the remaining area between the movable scroll and the fixed scroll is referred to as a "high pressure area" for the purpose of distinguishing the "low pressure area".

A scroll compressor according to a first embodiment of the present invention will be described in detail with reference to fig. 1 to 3.

FIG. 2a illustrates a partial cross-sectional view of a non-orbiting scroll provided with a fluid passageway in accordance with a first embodiment of the present invention; FIG. 2b shows an enlarged partial view of the fluid pathway of FIG. 2a including a one-way valve; fig. 3 shows a schematic plan view of a non-orbiting scroll according to a first embodiment of the present invention.

In the first embodiment, one fluid passage 13 is provided in the fixed scroll 22. As shown in fig. 2a, a one-way valve V is provided in the fluid passage 13. The fluid passage 13 is in particular provided in the non-orbiting scroll end plate 221 and has a low Wen Kongkou opening onto the low-pressure region DL defined by the non-orbiting scroll wrap S2 and the orbiting scroll wrap S4 in the compression mechanism CM on one side of the non-orbiting scroll end plate 221, as better shown in fig. 3, the location of this low-temperature orifice 130 in the low-pressure region DL (hatched portion in fig. 3, region located radially outward of the non-orbiting scroll 22 as shown in fig. 2 a), preferably this low-temperature orifice 130 is closer to the intake port of the compression mechanism CM, i.e. at the radially outward wrap end S0 of the non-orbiting scroll wrap S2, in certain operating conditions where liquid refrigerant may appear which flashes resulting in a larger local temperature difference, thus providing the low-temperature orifice 130 in a position close to said intake port, facilitating more efficient compensation of the local temperature difference. The fluid passage 13 further comprises a height Wen Kongkou on the other side of the fixed scroll end plate 221, which height Wen Kongkou opens towards a selected high temperature fluid source, which in this embodiment is preferably a back pressure chamber B (as shown in fig. 1) provided at said other side of the fixed scroll end plate 221, which back pressure chamber B, although not shown in the figures, is in fluid communication with a high pressure region DH (as the non-hatched part in fig. 3, the region located radially inside the fixed scroll 22 as shown in fig. 2 a) of the compression mechanism CM defined by the fixed scroll wrap S2 and the movable scroll wrap S4, such that the back pressure chamber B has an intermediate pressure higher than the suction pressure and lower than the discharge pressure. As shown in fig. 1, the high Wen Kongkou 132 of the fluid passage 13 is located in the cavity region of the back pressure chamber B, and since the pressure of the back pressure chamber B is higher than that of the low pressure region DL, fluid having a relatively high temperature in the back pressure chamber B tends to enter the low pressure region DL via the fluid passage 13.

Specifically, regarding the back pressure chamber B, which is constituted by a groove and a floating seal provided on the fixed scroll end plate 221 as exemplified by the scroll compressor of the floating fixed scroll shown in fig. 1, the back pressure chamber B is preferably fluidly connected to a medium pressure chamber having a medium pressure higher than the suction pressure and lower than the discharge pressure in the high pressure region DH defined in the compression mechanism CM so as to have the same medium pressure as the medium pressure chamber, thereby flexibly engaging the movable scroll 24 and the fixed scroll 22 with each other to provide a certain axial flexibility to protect the movable scroll 24 and the fixed scroll 22 from severe abrasion due to the rigid engagement under specific conditions (e.g., entry of impurity particles into the compression mechanism). Therefore, the fluid in the back pressure chamber B is a high-temperature and high-pressure fluid with respect to the fluid in the low-pressure region DL due to a certain compression, so that temperature compensation can be provided for the low-pressure region DL.

The opening and closing of the fluid passage 13 is controlled by providing a check valve V in the fluid passage 13. Fig. 2b shows an enlarged partial view of the one-way valve V arranged in the fluid passage 13. As shown in the figure, in the present embodiment, the check valve V is a mechanical valve constituted by an elastic assembly and includes the following components: a spring P, a spacer K, a stopper T, and an end cap G, wherein a reamer part 134 for accommodating the above-mentioned respective components is provided in the fluid passage 13, the reamer part 134 radially expands with respect to the low Wen Kongkou to form a stepped part e, and the reamer part 134 extends from the stepped part e to the high Wen Kongkou 132, thereby accommodating the respective components of the check valve V in the reamer part 134 as follows: one end of the helical spring P abuts and seats on the step e, the other end of the spring P abuts and carries a spacer K which further carries a stop T, and the end cap G is secured to the fluid passageway 13 at the elevation Wen Kongkou 132, for example by interference fit, adhesive bonding, welded bonding, riveting or the like, to thereby confine the various components within the counterbore portion 134 of the fluid passageway 13.

Specifically, as shown in fig. 2b, the blocking member T preferably has a spherical shape, the spacer K is shaped to stably support the blocking member T and to ensure that the through hole at the center of the spacer K is in fluid communication with the central through hole of the end cap G, which is a cylindrical member having a longitudinal section of a substantially "T" shape with the central through hole, and the lower end portion of the end cap G (the end portion in contact with the blocking member T) is shaped to be capable of engaging with the spherical surface of the blocking member T to form an airtight seal. In a normal state of being free from the external force, the spring P has a pre-compression amount according to the actual application requirement and presses the pad K to further press the blocking member T against and engage the lower end portion of the end cap G, so that the blocking member T is brought into airtight sealing engagement with the peripheral portion of the orifice G0 of the lower end portion of the end cap G, thereby closing the through hole in the center of the end cap G, thereby closing the fluid passage 13. The pre-pressing force provided by the spring P depends on the spring coefficient of the spring P itself and the pre-compression amount, and by setting the pre-compression amount or selecting springs of different spring coefficients, it is possible to set the value of the pre-pressing force provided by the spring P, and when the pressure difference between the back pressure chamber B and the low pressure region DL is greater than the value of the pre-pressing force provided by the spring P, i.e., the predetermined pressure difference, the pressure in the back pressure chamber B dominates and forces the blocking member T to move away from the end cap G in a direction to further compress the spring P, thereby opening the orifice G0 at the lower end portion of the end cap G, and the fluid enters the center through hole of the pad K via the gap between the blocking member T and the orifice G0 and reaches the low Wen Kongkou via the space near the spring P, thereby entering the low pressure region DL.

In practical applications, for example, due to different compression ratios under different working conditions, different suction pressures of the working fluid to be compressed, and the like, it is necessary to adjust the value of the pre-pressing force (predetermined pressure difference) provided by the spring P to control the timing and flow rate of the high-temperature and high-pressure fluid in the back pressure chamber B flowing into the low pressure region DL, and the like. This can be achieved by changing the spring or changing the pre-compression of the spring, wherein for the above described embodiments the pre-compression of the spring can be changed by changing the height of the spacer K. Also, the spacer K can compensate for the lack of the spring length, and in some cases, the spacer K can be omitted (see the exemplary check valve shown in fig. 6).

Fig. 4a shows a partial cross-sectional view of a non-orbiting scroll provided with a fluid passage according to a second embodiment of the present invention. Fig. 4b shows an enlarged partial view of the fluid pathway of fig. 4a including a one-way valve. The second embodiment is a modification of the first embodiment described above and is applicable to the case of a high-pressure side scroll compressor, and differs from the configuration of the first embodiment in that: the fluid passage 13 takes an "L" shaped path and extends from the low pressure region DL to a radial side surface of the non-orbiting scroll 22, a reaming portion 134 in the fluid passage 13 extends laterally in a radial direction of the non-orbiting scroll 22, and a check valve V is disposed laterally in the reaming portion 134. In the second embodiment, since the compression mechanism CM is located in the high-pressure space (having the discharge pressure), the fluid passage 13 in this embodiment is capable of introducing the high-temperature and high-pressure fluid in the high-pressure space into the low-pressure region DL to compensate for the local temperature difference in the low-pressure region DL.

In the second embodiment, the structure of the check valve V itself is substantially the same as that of the first embodiment, with the following minor modifications: as shown in fig. 4b, since the check valve V is laterally disposed in the reaming portion 134, the stepped portion e in the first embodiment is eliminated, the spring P directly abuts against the longitudinal bottom wall of the reaming portion 134, and in addition, the end cap G is modified to a cylindrical member having a central through hole, and the end cap G itself has a larger outer diameter and inner diameter than the first embodiment, i.e., the central through hole aperture of the end cap G becomes larger, which means that the aperture G0 of the end cap G engaged with the blocking member T becomes larger, so that when the blocking member T is moved away from the aperture G0 to open the fluid path, when the gap space between the blocking member T and the aperture G0 becomes larger, and thus more high temperature fluid per unit time will flow into the fluid passage 13 via the gap and into the low pressure region DL, thus enabling a faster and efficient balancing of the local temperature difference. Likewise, properly changing the pore size of the low temperature orifice 130 and the high Wen Kongkou orifice 132 can also adjust the amount of high temperature fluid into the low pressure region DL to some extent.

Likewise, the configuration of the second embodiment is also applicable to the case of the low-pressure side scroll compressor. At this time, since the compression mechanism CM is located in the low-pressure space V1 (having the exhaust pressure, as shown in fig. 1), the external conduit may be fixedly connected to the high Wen Kongkou of the fluid passage 13 or the central through hole of the cover plate G based on the fluid passage 13 in the second embodiment, that is, the high-temperature and high-pressure fluid in the high-pressure space V2 (as shown in fig. 1) may be guided into the low-pressure region DL. Still alternatively, the external conduit may be fluidly connected to an external high temperature fluid path of a system including the high pressure side/low pressure side scroll compressor to supply high temperature and high pressure fluid to the low pressure region DL, and so on, and various other modifications are possible as long as the supply of high temperature fluid to the low pressure region DL can be achieved to compensate for local temperature differences.

In another embodiment, not shown, the high-temperature fluid in the high-pressure region DH may also be supplied into the low-pressure region DL. For example, based on the foregoing first embodiment, referring to the configuration shown in fig. 2a, as long as the fluid passage 13 is modified to be in fluid communication from the high pressure region DH to the low pressure region DL, for example, the fluid passage 13 may have a "zigzag" or the like path in which the low temperature orifice 130 opens toward the low pressure region DL, the high Wen Kongkou opening toward the high pressure region DH, a passage extending generally in the radial direction of the non-orbiting scroll 22 communicates between the low temperature orifice 130 and the high Wen Kongkou 132, a check valve may be longitudinally arranged in the fluid passage 13 as in the first embodiment or laterally arranged in the fluid passage 13 as in the second embodiment, and a predetermined differential pressure is appropriately set as described above.

In the foregoing embodiments, the check valves V each include the same components, and the stoppers T each have a spherical shape, but the present invention is not limited thereto. Fig. 5 shows a check valve according to a third exemplary embodiment of the present invention. As shown, the check valve V of the third exemplary embodiment includes: an end cap G similar to that in the second embodiment; a blocking member T in the shape of an umbrella disk; and a coil spring P. It can be seen that the spacer is omitted in this embodiment, and the difference is that: the umbrella-shaped blocking member T has a longitudinal section of "umbrella shape", one end of which has a smaller outer diameter and is inserted in one end of the spring P to be fixed with respect to the spring P, and the "umbrella face" portion of the other end has a conical end face which forms a hermetically sealed abutment with the aperture G0 of the end cap G. Likewise, the predetermined pressure difference may be appropriately set as described above to define the inflow amount of the high-temperature fluid. This configuration is simpler, easier to install, and the direct connection of the blocking member T to the spring P allows for a more precise control and a quicker response, due to the omission of the spacer.

In addition, fig. 6a shows a partial cross-sectional view of a non-orbiting scroll provided with a fluid passage according to a fourth embodiment of the present invention; and FIG. 6b shows an enlarged partial view of the fluid pathway of FIG. 6a including a one-way valve.

The fourth embodiment is a modification of the foregoing first embodiment, differing mainly in the modification of the check valve V. As shown in the figure, the check valve V in the fourth embodiment includes: the elastic valve plate V1, the elastic valve plate V1 is a sheet member made of a material having elastic deformation properties, such as elastic metal, alloy, composite material, or the like; a valve gear V2, one side surface of the valve gear V2 being an arc surface as shown in the figure; and a valve cover V3 including a through hole offset from the central axis, wherein the valve sheet V1 is interposed between the valve stopper V2 and the valve cover V3, and the valve stopper V2 and the valve cover V3 clamp and fix the valve sheet V1 therebetween at one end (a left end shown in fig. 6 b), the through hole of the valve cover V3 is close to the other end (a right end shown in fig. 6 b) distant from the end, and the arcuate surface of the valve stopper V2 is distant from the valve cover V3 and the valve sheet V1 at the other end to form an upper space h such that the valve sheet V1 can be distant from the valve cover V3 within a certain range (a range from a lower surface of the valve cover V3 to the arcuate surface of the valve stopper V2). On the other hand, the fluid passage 13 in the non-orbiting scroll 22 also includes a counterbore portion 134 for receiving the check valve V, and the valve cover V3 may likewise be secured to the high Wen Kongkou of the fluid passage 13 by interference fit, adhesive bonding, weld bonding, staking, or the like to retain the valve plate V1 and valve rail V2 within the counterbore portion 134 of the fluid passage 13. Further, in addition to forming the stepped portion e as in the first embodiment, a shoulder f, which is annular flange-like in this embodiment, is included at the bottom of the reaming portion 134, the valve stage V2 is seated on the shoulder f so that there is a lower gap j with the stepped portion e, and the valve stage V2 is shaped so that the lower gap j is in fluid communication with an upper space h above the valve stage V2.

Normally, the valve plate V1 abuts against the valve cover V3 and seals the orifice V0 covering the through hole. By selecting the material of the valve plate V1 to select the elastic deformation coefficient, the force required for the valve plate V1 to elastically deform can be defined, so that the predetermined differential pressure is defined as described above, that is, when the pressure difference between the high temperature fluid source (e.g., the back pressure chamber B) and the low pressure region DL is greater than the force required for the valve plate V1 to elastically deform, that is, the predetermined differential pressure, the pressure in the back pressure chamber B dominates and forces the valve plate V1 to elastically deform away from the orifice V0 to open the orifice V0, and the fluid enters the upper space h through the gap between the valve plate V1 and the orifice V0 and reaches the low Wen Kongkou through the lower gap j to enter the low pressure region DL. The valve gear V2 can limit the elastic deformation degree of the valve plate V1, so as to limit the opening size of the orifice V0, and make the valve plate V1 recover faster and more sensitive.

In addition, in other embodiments not shown, the check valve may have other configurations, for example, based on the fourth embodiment, the valve stage V2 may be omitted, the valve plate V1 may be fixed to the valve cover V3 at one end by means of screw engagement, welding engagement, riveting, or the like, without providing the valve stage V2, and the above technical effects may be achieved.

Although in the above embodiment, the fluid passage and the check valve are both provided in the non-orbiting scroll 22, it will be understood by those skilled in the art that since the orbiting and non-orbiting scrolls together define a low pressure region DL, the low pressure region DL is located in the space between the orbiting and non-orbiting scrolls, a similar fluid passage 13 may be provided in the orbiting scroll 24 and may also be in fluid communication to the low pressure region DL, or the fluid passage may be located in the orbiting scroll in one section and in the non-orbiting scroll in another section, so long as it is possible to deliver high temperature fluid from various high temperature fluid sources such as those described above into the low pressure region DL.

Further, although the back pressure chamber B is shown on the fixed scroll end plate in the foregoing embodiment, in the case of a scroll compressor such as a floating orbiting scroll, the back pressure chamber B may be provided in the back side of the orbiting scroll end plate 241. Therefore, the high-temperature fluid in the back pressure chamber on the orbiting scroll end plate 241 can also be supplied into the low-pressure region DL by providing a fluid passage in the orbiting scroll end plate 241.

Although the exemplary embodiments of the scroll compressor according to the present invention have been described in the foregoing embodiments, the present invention is not limited thereto, but various modifications, substitutions and combinations may be made without departing from the scope of the present invention.

It is obvious that various embodiments can be further devised by combining or modifying the different embodiments and the respective technical features in different ways.

The scroll compressor according to the preferred embodiment of the present invention has been described above in connection with the specific embodiment. It will be understood that the above description is by way of example only and not by way of limitation, and that various modifications and alterations will occur to those skilled in the art in light of the above description without departing from the scope of the invention. Such variations and modifications are intended to be included within the scope of the present invention.

Claims

1. A scroll compressor (1) comprising a Compression Mechanism (CM) adapted to compress a working fluid and comprising:

a non-orbiting scroll (22) including a non-orbiting scroll end plate (221) and a non-orbiting scroll wrap (S2) extending from a first side of the non-orbiting scroll end plate; and

An orbiting scroll (24) including an orbiting scroll end plate (241) and an orbiting scroll wrap (S4) extending from a first side of the orbiting scroll end plate,

Wherein a suction chamber and a series of closed chambers are defined between the fixed scroll wrap and the movable scroll wrap and a low pressure region (DL) having a suction pressure and a remaining high pressure region (DH) are formed, wherein the low pressure region (DL) includes the suction chamber and a low pressure chamber having a suction pressure adjacent to the suction chamber among the closed chambers,

Wherein the scroll compressor further comprises at least one fluid passage (13) configured to introduce a high temperature fluid having a temperature higher than that in the low pressure region into the low pressure region and a check valve (V) arranged to control opening and closing of the fluid passage.

2. The scroll compressor of claim 1, wherein the one-way valve is configured to: opening the fluid passage to allow the high-temperature fluid to enter the low-pressure region when a difference between the pressure of the high-temperature fluid and the suction pressure in the low-pressure region is equal to or greater than a predetermined differential pressure; and closing the fluid passage to prevent the high temperature fluid from entering the low pressure region when a difference between the pressure of the high temperature fluid and the suction pressure in the low pressure region is less than the predetermined pressure difference.

3. The scroll compressor of claim 2, wherein the fluid passageway introduces the high temperature fluid at the high pressure region to the low pressure region.

4. The scroll compressor according to claim 2, wherein said fluid passageway introduces said high temperature fluid in a back pressure chamber (B) to said low pressure region.

5. The scroll compressor of claim 4, wherein the back pressure chamber is disposed on a second side of the non-orbiting scroll end plate opposite the first side of the non-orbiting scroll end plate, the fluid passageway configured as a through hole disposed in the non-orbiting scroll end plate extending directly from the back pressure chamber to the low pressure region.

6. The scroll compressor of claim 2, wherein the fluid passageway is configured to introduce the high temperature fluid outside the compression mechanism, inside a housing (12) of the scroll compressor, to the low pressure region.

7. The scroll compressor of claim 2, wherein the fluid passageway is configured to introduce the high temperature fluid in a fluid line of a system including the scroll compressor to the low pressure region.

8. The scroll compressor of any one of claims 1-7, wherein the fluid passageway includes a low Wen Kongkou (130) opening toward the low-pressure region, the low-temperature orifice being proximate to an air inlet of the compression mechanism.

9. The scroll compressor of claim 8, wherein the low temperature aperture is disposed in the non-orbiting scroll end plate.

10. The scroll compressor of any of claims 1-7, wherein the one-way valve comprises:

an end cap (G) defining an aperture (G0) for passage of a fluid;

A blocking member (T); and

A spring (P),

11. The scroll compressor of any of claims 1-7, wherein the one-way valve comprises:

A valve cover (V3) defining an orifice (V0) for passage of a fluid; and

A valve plate (V1) one end of which is fixed relative to the valve cover,