CN210141195U

CN210141195U - Scroll compressor having a plurality of scroll members

Info

Publication number: CN210141195U
Application number: CN201920473117.XU
Authority: CN
Inventors: 刘轩; 金培
Original assignee: Emerson Climate Technologies Suzhou Co Ltd
Current assignee: Copeland Suzhou Co Ltd
Priority date: 2019-04-09
Filing date: 2019-04-09
Publication date: 2020-03-13
Anticipated expiration: 2029-04-09

Abstract

The utility model provides a scroll compressor, including compression mechanism, compression mechanism is suitable for the compression working fluid and include: the fixed scroll comprises a fixed scroll end plate and a fixed 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 fixed 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 utility model discloses a thereby the vortex compressor can solve the too big temperature fatigue stress in eliminating the vortex scroll of local difference in temperature of avoiding the fluid flash distillation problem, increase of service life greatly to simple structure, easily manufacturing have higher cost benefit.

Description

Scroll compressor having a plurality of scroll members

Technical Field

The utility model relates to a scroll compressor specifically relates to one kind and carries out the scroll compressor who improves in the local difference in temperature to the scroll among the 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 applications such as refrigeration systems, air conditioning systems, and heat pump systems. The scroll compressor includes a compression mechanism for compressing a working fluid (e.g., a refrigerant), the compression mechanism including an orbiting scroll including a fixed scroll end plate and a fixed scroll wrap extending from a side surface of the fixed scroll end plate, and a stationary scroll including an orbiting scroll end plate and an orbiting scroll wrap extending from the orbiting scroll end plate, wherein the orbiting scroll is held in stable engagement with the fixed scroll, and when the scroll compressor is in operation, the orbiting scroll performs an orbiting relative motion with respect to the fixed scroll such that the orbiting scroll wrap and the fixed scroll wrap are held 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 fixed 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, and finally the high-temperature and high-pressure fluid is discharged to the outside of the compression mechanism through the gas outlet on the fixed scroll end plate.

Flashing is often observed when scroll compressors are operated, particularly at high pressure ratio conditions. The liquid refrigerant is mixed in the gaseous refrigerant and then enters the suction chamber of the compression mechanism where it flashes and thus rapidly absorbs the temperature in the suction chamber. Therefore, the temperature in the suction chamber is suddenly decreased, so that the temperature difference between both sides of the scroll wrap is increased, and the scroll wrap is cracked or even failed.

Accordingly, there is a need to provide a scroll compressor that can solve or mitigate the problem of flash evaporation damage to the scroll wraps in the compressor mechanism.

SUMMERY OF THE UTILITY MODEL

The general outline of the present invention is provided in this section, not a full scope of the invention or a full disclosure of all the features of the invention.

The object of the present invention is to improve upon one or more of the above mentioned technical problems. In general, the utility model discloses a great deal of research has been carried out to the problem of above-mentioned working fluid flash distillation to develop the scroll compressor that can effectively avoid or show the emergence that reduces the fluid flash distillation thereby basically eliminate the too big problem of the local difference in temperature in the compression mechanism, thereby avoid the damage of temperature fatigue stress in the scroll to the compression mechanism as follows.

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

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 non-orbiting scroll wrap and the orbiting 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 provided to control opening and closing of the fluid passage.

By providing the above-mentioned fluid passage to supply high temperature fluid to said 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 drops and thereby avoiding fatigue stresses due to local temperature differences.

According to an aspect of the present invention, the check valve is an electromagnetic valve or a mechanical valve and is provided in the fluid passage, the check valve is configured to: opening the fluid passage to allow the high-temperature fluid to enter the low-pressure region when a difference between a pressure of the high-temperature fluid and a suction pressure in the low-pressure region is equal to or greater than a predetermined pressure difference; 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 opens and the opening period can be appropriately defined according to the actual application by setting the predetermined pressure difference, thereby controlling the supply amount of the high-temperature fluid.

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

According to an aspect of the present invention, the fluid passage introduces the high temperature fluid located in the high pressure region to the low pressure region.

According to an aspect of the present invention, the fluid passage introduces the high temperature fluid located in a back pressure chamber to the low pressure region.

According to an aspect of the present invention, the back pressure chamber is provided on a second side of the non-orbiting scroll end plate opposite to the first side of the non-orbiting scroll end plate, the fluid passage is configured to be provided in the non-orbiting scroll end plate from the back pressure chamber directly extends to the through hole of the low pressure region.

According to an aspect of the present invention, the fluid passage is configured to introduce the high-temperature fluid outside the compression mechanism, inside a casing of the scroll compressor, to the low-pressure region.

According to one aspect of the present invention, the fluid passage 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 an aspect of the invention, the fluid passage comprises a low temperature orifice opening towards the low pressure region, the low temperature orifice being close to an air inlet of the compression mechanism.

According to an aspect of the present invention, the low temperature orifice is provided in the non-orbiting scroll end plate.

According to an aspect of the present invention, the check valve includes:

an end cap defining an aperture for passage of fluid;

a blocking member; and

a spring is arranged on the upper surface of the shell,

wherein the spring urges the barrier into abutment 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 wherein 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 an aspect of the present invention, the check valve includes:

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 a hermetic 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 the valve sheet is elastically deformed to be separated 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 difference.

To sum up, according to the utility model discloses a scroll compressor provides following beneficial effect at least: according to the utility model discloses a thereby scroll compressor can solve the fluid flash distillation problem and avoid the too big and then eliminated the temperature fatigue stress in the vortex scroll of the local difference in temperature in the compression mechanism, increase of service life greatly, and the utility model discloses a scroll compressor simple structure, easily manufacturing have higher cost-effectiveness.

Drawings

The foregoing and additional features and characteristics of the present invention will become more apparent from the following detailed description, taken with reference to the accompanying drawings, which are given by way of example only and which are not necessarily drawn to scale. Like reference numerals are used to indicate like parts in the accompanying drawings, in which:

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

figure 2a shows a cross-sectional view of a non-orbiting scroll provided with a fluid passage according to a first embodiment of the present invention;

FIG. 2b shows an enlarged partial view of the fluid path of FIG. 2a including the check valve;

fig. 3 shows a schematic bottom view of a non-orbiting scroll according to a first embodiment of the present invention;

figure 4a shows a 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 passageway of FIG. 4a including the one-way valve;

figure 5 shows a one-way valve in the fluid path of a non-orbiting scroll according to a third embodiment of the present invention;

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 a close-up view of the fluid path of fig. 6a including the one-way valve.

List of reference marks

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

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

A low-pressure space a 1; plenum a 2; a drive shaft 16; main bearing seat 40

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

Non-orbiting scroll wrap S2; an orbiting scroll end plate 241; orbiting scroll wrap S4

A fluid passage 13; a low temperature vent 130; a high temperature orifice 132; scroll end S0

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

End cap G, stop piece T, spring P, cushion block K and hole G0

The valve plate V1; valve gear V2; a valve cover V3; port V0; a lower gap j; upper interval h

Detailed Description

A preferred embodiment 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 not intended to limit the present disclosure, application, or uses.

For convenience of description, the scroll compressor shown in fig. 1 is exemplarily illustrated as a low pressure side scroll compressor, i.e., the 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, in which the compression mechanism is located in a high pressure space. This will be described in detail below.

Figure 1 shows a longitudinal cross-sectional view of a scroll compressor according to the present invention. First, an overall structure of a scroll compressor according to the present invention is described in brief with reference to fig. 1.

As shown in fig. 1, the scroll compressor 1 includes a substantially 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., a 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. Lubricant, such as lubricating oil, may be stored in oil sump O within the bottom of housing 12 for lubricating the various components of scroll compressor 1 (e.g., orbiting scroll 24, non-orbiting scroll 22, thrust plate, etc.).

The scroll compressor 1 further includes a partition plate 19 disposed between the top cover 26 and the housing 12 to partition an internal space of the scroll compressor 1 into a high-pressure space a2 and a low-pressure space a 1. Partition 19 and cover 26 define a high pressure space a2 therebetween, and partition 19, housing 12 and base 28 define a low pressure space a1 therebetween. An intake pipe 18 for introducing a low-pressure working fluid to be compressed is provided on the casing 12 at the low-pressure space a1, and an exhaust pipe 17 for discharging a compressed high-temperature and high-pressure fluid to the outside of the scroll compressor 1 is provided in the high-pressure space a 2. 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 a 1.

The compression mechanism CM includes an orbiting scroll 24 and a non-orbiting scroll 22. The non-orbiting scroll 22 includes a non-orbiting scroll end plate 221 and a non-orbiting scroll wrap S2; orbiting scroll 24 includes an orbiting scroll end plate 241, an orbiting scroll wrap S4 extending from a first side of the driven scroll end plate 241, and a hub 240 extending from a second side of the driven scroll end plate 241. Defined within the compression mechanism CM are: an open suction chamber in fluid communication with the outside of the compression mechanism CM, the inlet of said suction chamber being in fluid communication with the low-pressure space a1 inside the casing 12 so as to introduce the working fluid to be compressed in the low-pressure space a1 into the compression mechanism CM; a series of closed chambers formed by the engagement of the non-orbiting and orbiting scroll wraps (described in detail below); 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 casing 12 and discharging the compressed high temperature and high pressure fluid into the high pressure space a 2.

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 also introduces the low-pressure working fluid from the low-pressure space and discharges the compressed high-temperature high-pressure fluid to the high-pressure space, so 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 mainly lies in the difference of the space pressure where the compression mechanism CM is located, and the description thereof is omitted.

The electric motor includes 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 axis of rotation relative to the housing 12. Drive shaft 16 may include an eccentric pin mounted to or integrally formed with a first end (tip) of 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 in the drawings) extending upward from the central hole to an end surface of the eccentric pin. The end (lower end) of the central bore may be immersed in an oil sump O at the bottom of the housing 12 of the scroll compressor 1 so that lubricating oil can be delivered from the sump O, for example under the action of centrifugal force generated by rotation of the drive shaft 16, and caused to flow upwardly through the central bore and eccentric bore and out the end surface of the eccentric pin.

The lubricating oil that flows out from the end surface of the eccentric pin can flow into, for example, 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. The lubricating oil in this lubricating oil supply region may lubricate, for example, the rotating joints 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 may also be supplied to the compression mechanism CM.

Orbiting scroll 24 is axially supported by main bearing housing 40 and is supported by main bearing housing 40 so as to be able to orbit. 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 bushing or bearing.

The non-orbiting scroll 22 is mounted to the main bearing housing 40 using, for example, mechanical fasteners. The orbiting scroll 24 is driven by an electric motor via the drive shaft 16 (specifically, an eccentric pin) so as to be capable of translational rotation, i.e., orbiting, relative to the non-orbiting scroll 22 (i.e., the axis of the orbiting scroll 24 orbits relative to the axis of the non-orbiting scroll 22, but both the orbiting and

non-orbiting scrolls

24, 22 do not themselves rotate about their respective axes) by means of an oldham ring. Thus, the chambers defined by the non-orbiting scroll wrap S2 and the orbiting scroll wrap S4 are changed from the open suction chamber to a series of closed chambers as follows in moving from the radially outer side to the radially inner side: the outer low pressure chamber is changed into a middle medium pressure compression chamber (the pressure is greater than the suction pressure and less than the discharge pressure) and then is changed into a high pressure compression chamber at the center (the high pressure is the highest pressure, namely equal to the discharge pressure), and the volume of the chamber is gradually reduced from large to small. In this way, the pressure of the fluid is also gradually increased, 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 above-mentioned chambers, the open suction chamber has a suction pressure, and in the series of closed chambers formed there is a low pressure chamber having a suction pressure as follows: the low-pressure chamber having suction pressure is a closed low-pressure chamber having suction pressure adjacent to the suction chamber defined instantaneously by the engagement of the orbiting scroll wrap S4 with the non-orbiting scroll wrap S2 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 low pressure chamber having the closing instant of the suction pressure is referred to as a "low pressure area" having the suction pressure, and the remaining area between the orbiting scroll and the non-orbiting scroll is referred to as a "high pressure area" in order to distinguish 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.

Figure 2a shows a partial cross-sectional view of a non-orbiting scroll provided with a fluid passage according to a first embodiment of the present invention; FIG. 2b shows an enlarged partial view of the fluid path of FIG. 2a including the check 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 non-orbiting scroll 22. As shown in fig. 2a, a check valve V is provided in the fluid passage 13. Fluid passage 13 is specifically provided in non-orbiting scroll end plate 221 and has a low temperature orifice 130 located on one side of non-orbiting scroll end plate 221 opening toward low pressure region DL defined by non-orbiting scroll wrap S2 and orbiting scroll wrap S4 in compression mechanism CM, as better shown in fig. 3, the location of the low temperature orifice 130 in the low pressure region DL (the hatched portion in fig. 3, the region radially outward of the non-orbiting scroll 22 as shown in fig. 2 a), preferably, the low temperature port 130 is located closer to the intake port of the compression mechanism CM, i.e., the scroll end S0 radially outward of the non-orbiting scroll wrap S2, under certain operating conditions, liquid refrigerant can appear in the air inlet area, the liquid refrigerant flashes to cause a large local temperature difference, thus, locating the low temperature vent 130 close to the inlet port facilitates more efficient compensation of localized temperature differences. The fluid passage 13 further includes a high temperature orifice 132 on the other side face of the non-orbiting scroll end plate 221, the high temperature orifice 132 being open to a selected high temperature fluid source, which in the present embodiment is preferably a back pressure chamber B (shown in fig. 1) provided at the other side face of the non-orbiting scroll end plate 221, although not shown in the drawings, in fluid communication with a high pressure region DH (a non-hatched portion in fig. 3, a region located radially inward of the non-orbiting scroll 22 as shown in fig. 2 a) defined by the non-orbiting scroll wrap S2 and the orbiting scroll wrap S4 in the compression mechanism CM, 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 temperature orifice 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 the pressure of the low pressure region DL, the 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, exemplified by the scroll compressor of the floating non-orbiting scroll shown in fig. 1, which is constituted by a groove provided on the non-orbiting scroll end plate 221 and a floating seal ring, wherein the back pressure chamber B is preferably fluidly connected to an intermediate pressure chamber having an intermediate pressure higher than a suction pressure and lower than a discharge pressure in a high pressure region DH defined in the compression mechanism CM so as to have the same intermediate pressure as the intermediate pressure chamber, so that the orbiting scroll 24 and the non-orbiting scroll 22 are flexibly engaged with each other to provide a certain axial flexibility to protect the orbiting scroll 24 and the non-orbiting scroll 22 from severe wear due to the rigid engagement under certain circumstances (e.g., entry of foreign 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 the 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 a close-up view of the one-way valve V arranged in the fluid passage 13. As shown in the drawing, in the present embodiment, the check valve V is a mechanical valve constituted by an elastic member and includes the following components: spring P, spacer K, stopper T and end cap G, wherein a counterbore portion 134 is provided in fluid passage 13 for accommodating the above components, counterbore portion 134 expands radially with respect to low temperature orifice 130 to form a step e, and counterbore portion 134 extends from step e to high temperature orifice 132, so as to accommodate the components of check valve V in counterbore portion 134 in the following manner: one end of the helical spring P abuts and seats against the step e and the other end of the spring P abuts and bears against a spacer K which further bears against the barrier member T, and an end cap G is secured to the fluid passageway 13 at the high temperature orifice 132, for example by interference fit, adhesive bonding, welded bonding, riveting or the like so as to confine the various components within the counterbore portion 134 of the fluid passageway 13.

Specifically, as shown in FIG. 2b, the barrier T preferably has a spherical shape, the head block K is shaped to stably support the barrier T and to ensure that the through-hole at the center of the head block K is in fluid communication with the central through-hole of the end cap G, the end cap G is a cylindrical member having a central through-hole with a longitudinal cross-section that is generally "T" shaped, and the lower end portion of the end cap G (the end in contact with the barrier T) is shaped to engage the spherical surface of the barrier T to form a gas-tight seal. In a normal state without external force, spring P has a pre-compression amount according to the actual application requirements and urges the pad K to further urge the stopper T against and into engagement with the lower end portion of end cap G, so that the stopper T is brought into airtight sealing engagement with the peripheral portion of the orifice G0 of the lower end portion of end cap G to close the through hole in the center of end cap G, thereby closing the fluid passage 13. The pre-compression force provided by the spring P depends on the spring rate of the spring P itself and the pre-compression amount, and by setting the pre-compression amount or selecting springs of different spring rates, the value of the pre-compression force provided by the spring P can be set, when the pressure difference between the back pressure chamber B and the low pressure region DL is greater than the value of the pre-compression force provided by the spring P, i.e. a predetermined pressure difference, then the pressure in the back pressure chamber B dominates and forces the blocking member T away from the end cap G to move in a direction to further compress the spring P, thereby opening the orifice G0 of said lower end portion of the end cap G, and the fluid enters the central through hole of the spacer K via the gap between the blocking member T and the orifice G0 and reaches the low temperature orifice 130 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 operating 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 pressure (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. This can be achieved by replacing the spring or by changing the precompression of the spring, which can be changed by changing the height of the head block K for the above-described embodiment. Also, the spacer K can compensate for the lack of 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 a close-up view of the fluid path of fig. 4a including the one-way valve. The second embodiment is a modification on the first embodiment described above and is applied 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 counterbore 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 counterbore 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 can introduce the high-temperature and high-pressure fluid in the high-pressure space into the low-pressure region DL in this embodiment 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 slight modifications: as shown in fig. 4b, since the check valve V is transversely disposed in the counterbore portion 134, the step e in the first embodiment is eliminated, the spring P directly abuts against the longitudinal bottom wall of the counterbore portion 134, and in addition, the end cap G is modified into a cylindrical member having a central through hole, and the end cap G itself has a larger outer and inner diameter than in the first embodiment, that is, the central through hole diameter of the end cap G becomes larger, which means that the orifice G0 of the end cap G that engages with the stopper T becomes larger, so that when the stopper T is opened away from the orifice G0 to open the fluid path, the clearance space between the stopper T and the orifice G0 becomes larger, and thus more high-temperature fluid per unit time will flow into the fluid passage 13 via the clearance and into the low-pressure region DL, and thus the local temperature difference can be balanced more quickly and efficiently. Likewise, appropriately changing the bore diameters of the low temperature orifice 130 and the high temperature orifice 132 may also adjust the amount of high temperature fluid entering 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 discharge pressure, as shown in fig. 1), it is possible to fixedly connect the external conduit with the high temperature orifice 132 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, and at the same time, to guide the high temperature and high pressure fluid in the high pressure space V2 (as shown in fig. 1) into the low pressure region DL. Still alternatively, the above-mentioned outboard conduit may be fluidly connected to an external high temperature fluid path of the 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 to compensate for local temperature differences can be achieved.

In another embodiment, not shown, the high temperature fluid in the high pressure zone DH may also be supplied into the low pressure zone 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 fluidly communicated from the high pressure region DH to the low pressure region DL, for example, the fluid passage 13 may have a path of a zigzag shape or the like in which the low temperature orifice 130 opens toward the low pressure region DL and the high temperature orifice 132 opens toward the high pressure region DH, and a passage extending generally in the radial direction of the non-orbiting scroll 22 communicates between the low temperature orifice 130 and the high temperature orifice 132, and a check valve may be disposed longitudinally in the fluid passage 13 as in the first embodiment or transversely in the fluid passage 13 as in the second embodiment, and the predetermined pressure difference is set appropriately as described previously.

In the foregoing embodiments, the check valves V each include the same components, and the stoppers T are each in a spherical shape, but the present invention is not limited thereto. Fig. 5 shows a non-return valve according to a third exemplary embodiment of the present invention. As shown, the check valve V of the third exemplary embodiment includes: end cap G similar to that of the second embodiment; an umbrella-shaped barrier member T; and a coil spring P. As can be seen, the spacers are omitted in this embodiment and differ in that: the baffle T, which is in the form of an umbrella, has a longitudinal section in the form of an "umbrella" with one end having a smaller external diameter and inserted in one end of the spring P to be fixed with respect to the spring P, and with the "canopy" portion of the other end having a conical end face which comes into airtight sealed abutment with the orifice G0 of the end cap G. Also, the predetermined pressure difference may be appropriately set as previously described to define the inflow amount of the high-temperature fluid. This configuration is simpler and easier to install, as the spacer is omitted, and the direct connection of the stop T to the spring P makes the control more precise and the response faster.

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 figure 6b shows a close-up view of the fluid path of figure 6a including the one-way valve.

The fourth embodiment is a modification based on the foregoing first embodiment, and differs mainly in the modification of the check valve V. As shown, the check valve V in the fourth embodiment includes: the elastic valve sheet V1 and the elastic valve sheet V1 are sheet pieces made of materials with elastic deformation performance, such as elastic metal, alloy, composite materials and the like; a valve rail V2, one side of the valve rail V2 being an arcuate surface as shown; and a valve cover V3, the valve cover V3 including a through hole that is offset from the center axis, wherein the valve sheet V1 is interposed between the valve stop V2 and the valve cover V3, and the valve stop V2 and the valve cover V3 sandwich and fix the valve sheet V1 therebetween at one end (left end shown in fig. 6 b), the through hole of the valve cover V3 is close to the other end (right end shown in fig. 6 b) that is away from the end and the arcuate surface of the valve stop V2 is away from the valve cover V3 and the valve sheet V1 at the other end to form an upper space h, so that the valve sheet V1 can be away from the valve cover V3 within a range (from the lower surface of the valve cover V3 to the arcuate surface of the valve stop 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 temperature orifice 132 of the fluid passage 13 by interference fit, adhesive bonding, weld bonding, staking, etc. to confine the valve flap V1 and valve stop V2 within the counterbore portion 134 of the fluid passage 13. Further, in addition to forming the step e as in the first embodiment, the bottom of the counterbore portion 134 also includes a shoulder f, which in this embodiment is in the form of an annular flange, on which a valve stop V2 sits so that there is a lower gap j with the step e, and the valve stop V2 is shaped so that it is in fluid communication with the upper space h above the valve stop V2.

Normally, the valve sheet V1 abuts against the valve cover V3 and seals the orifice V0 covering the through hole. By selecting the material of the valve vane V1 to select the elastic deformation coefficient, the force required for elastic deformation of the valve vane V1 can be defined to define the predetermined pressure differential as described above, i.e., when the pressure difference between the high temperature fluid source (e.g., back pressure chamber B) and the low pressure region DL is greater than the force required for elastic deformation of the valve vane V1, i.e., the predetermined pressure differential, then the pressure in back pressure chamber B dominates and forces the valve vane V1 to elastically deform away from the orifice V0 opening the orifice V0, and the fluid enters the upper space h via the gap between the valve vane V1 and the orifice V0 and reaches the low temperature orifice 130 via the lower gap j and enters the low pressure region DL. The valve stop V2 can limit the elastic deformation degree of the valve sheet V1, so that the opening size of the orifice V0 is limited, and the valve sheet V1 is faster and more sensitive in recovery speed.

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

Although in the above described embodiment both the fluid passage and the one-way valve are provided in the non-orbiting scroll 22, it will be appreciated by those skilled in the art that since the orbiting and non-orbiting scrolls together define a low pressure region DL located in the space between the orbiting and non-orbiting scrolls, a similar fluid passage 13 may also be provided in the orbiting scroll 24 and may likewise be fluidly connected to the low pressure region DL, or the fluid passage may also be located in one section in the orbiting scroll and another section in the non-orbiting scroll, provided that it is possible to deliver high temperature fluid from various high temperature fluid sources such as those previously described 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, the back pressure chamber B may be provided in the back side of the orbiting scroll end plate 241 in the case of a scroll compressor such as a floating orbiting scroll. Therefore, the high-temperature fluid in the back pressure chamber on orbiting scroll end plate 241 can also be supplied into low-pressure region DL by providing a fluid passage in orbiting scroll end plate 241.

Although the exemplary embodiment of the scroll compressor according to the present invention has 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 further different embodiments can be devised by combining different embodiments and individual features in different ways or modifying them.

The scroll compressor according to the preferred embodiment of the present invention has been described above with reference to the specific embodiments. It will be understood that the above description is intended to be illustrative and not restrictive, and that various changes and modifications may be suggested to one skilled in the art in view of the above description without departing from the scope of the invention. Such variations and modifications are also intended to be included within the scope of the present invention.

Claims

1. A scroll compressor comprising a compression mechanism adapted to compress a working fluid and comprising:

a low pressure region having a suction pressure and a remaining high pressure region are formed between the non-orbiting scroll wrap and the orbiting scroll wrap,

characterized in that 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 one-way valve provided 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 a pressure of the high-temperature fluid and a suction pressure in the low-pressure region is equal to or greater than a predetermined pressure difference; 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 of claim 2, wherein the fluid passageway introduces the high temperature fluid located in a back pressure chamber to the low pressure region.

5. The scroll compressor of claim 4, wherein the back pressure cavity 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 passage configured as a through hole disposed in the non-orbiting scroll end plate extending directly from the back pressure cavity to the low pressure region.

6. The scroll compressor of claim 2, wherein the fluid passageway is configured to introduce the high temperature fluid inside a housing of the scroll compressor outside the compression mechanism 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 passage includes a low temperature orifice opening toward the low pressure region, the low temperature orifice being proximate an intake of the compression mechanism.

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

10. The scroll compressor of any one of claims 2-7, wherein the one-way valve comprises:

an end cap defining an aperture for passage of fluid;

a blocking member; and

a spring is arranged on the upper surface of the shell,

11. The scroll compressor of any one of claims 2-7, wherein 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,