CN217999879U - Compression mechanism and scroll compressor - Google Patents

Abstract

The utility model relates to a compression mechanism and scroll compressor, include: an orbiting scroll having an orbiting scroll end plate and an orbiting scroll blade formed at one side of the orbiting scroll end plate; a fixed scroll having a fixed scroll end plate and a fixed scroll blade formed at a first side of the fixed scroll end plate, the movable scroll blade and the fixed scroll blade engaging with each other to form a series of compression chambers between the movable scroll and the fixed scroll; wherein, compression mechanism is provided with flowing back passageway and flowing back control mechanism, and flowing back control mechanism is suitable for and makes pressure differential with passive mode for the flowing back passageway can provide fluid intercommunication according to selectively between the outside of first compression chamber in a series of compression chambers and compression mechanism the utility model discloses a scroll compressor can realize effective flowing back, simple structure, low cost.

Description

Compression mechanism and scroll compressor

Technical Field

The present invention relates to a compression mechanism, and more particularly, to a compression mechanism and a scroll compressor having a liquid discharge design.

Background

The statements in this section merely provide background information related to the present disclosure and may not constitute prior art.

Scroll compressors are known as compression machines of the capacity type. The scroll compressor includes a compression mechanism composed of a fixed scroll and a movable scroll. Generally, the fixed scroll and the orbiting scroll each include scroll blades, which are engaged with each other to form a series of compression chambers between the fixed scroll and the orbiting scroll to compress a working fluid, and compressed high-pressure gas is discharged through a discharge port at the center of the fixed scroll.

Conventional scroll compressors typically employ an axially compliant design, i.e., the non-orbiting and orbiting scrolls may be axially separated from one another by a distance for, for example, unloading high pressure fluid (such as gaseous refrigerant) or discharging excess liquid within the compression chambers (such as liquid refrigerant during initial startup of the compressor) when the pressure within the compression chambers is too high.

However, for a large-displacement scroll compressor, the axial separation distance of the compression mechanism is limited, even the design of axial flexibility is completely absent, so that liquid in the compression cavity cannot be discharged in time, and the situation that the scroll blade is subjected to great impact force under the working condition of liquid carrying is easy to happen, so that the scroll blade is cracked. In addition, still can produce very big moment of torsion in the twinkling of an eye at scroll compressor's start-up, produce certain impact to the motor, influence the life of the motor of working under the operating mode that frequently stops very easily.

Accordingly, there is a need for an improved drain design for scroll compressors, particularly large discharge scroll compressors.

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to provide a compression mechanism and scroll compressor with new flowing back design, this compression mechanism is provided with flowing back passageway and flowing back control mechanism, thereby can in time discharge the liquid that compresses the intracavity too much and effectively avoid scroll compressor's liquid to hit the damage to thereby can also reduce the start moment of torsion of compressor, reduce motor impact load and improve motor life.

Another object of the utility model is to provide a compression mechanism and scroll compressor with new flowing back design, this compression mechanism is provided with flowing back passageway and passive flowing back control mechanism, not only can effectively deal with the liquid operating mode of taking of compressor, need not in addition to set up independent power supply and need not to make pressure differential from the outside introduction fluid of compression mechanism for the flowing back, simple structure, spare part are few, processing is easy and low cost.

According to an aspect of the present invention, there is provided a compression mechanism, including: the movable vortex comprises a movable vortex end plate and movable vortex blades formed on one side of the movable vortex end plate; a fixed scroll having a fixed scroll end plate and a fixed scroll blade formed at a first side of the fixed scroll end plate, the movable scroll blade and the fixed scroll blade engaging with each other to form a series of compression chambers between the movable scroll and the fixed scroll; wherein the compression mechanism is provided with a liquid discharge channel and a liquid discharge control mechanism adapted to create a pressure differential in a passive manner such that the liquid discharge channel is capable of selectively providing fluid communication between a first compression chamber of the series of compression chambers and an exterior of the compression mechanism.

Optionally, the drain control mechanism comprises a piston disposed within the drain passage and movable under the influence of a pressure differential between an open position providing fluid communication and a closed position not providing fluid communication.

Optionally, a liquid drainage channel is provided in the non-orbiting scroll and configured to extend through the non-orbiting scroll generally in the axial direction of the compression mechanism, the liquid drainage channel including a piston bore section accommodating the piston and a liquid inlet section communicating the piston bore section with the first compression chamber, a side of the piston bore section having a liquid outlet communicating with the exterior of the compression mechanism.

Optionally, the liquid discharge control mechanism further comprises a cover covering and sealing the piston bore section, thereby forming a pressure control chamber in an area between the cover and the piston within the piston bore section.

Optionally, the liquid discharge control mechanism further includes a pressure control passage provided in the non-orbiting scroll, one end of the pressure control passage being communicated to a second compression chamber in the series of compression chambers, the other end of the pressure control passage being communicated to the pressure control chamber, the first compression chamber being closer to a radially outer side of the compression mechanism than the second compression chamber, and the pressure control passage having a throttle expansion structure.

Optionally, the first compression chamber is a suction chamber in the series of compression chambers or an intermediate compression chamber adjacent to the suction chamber.

Optionally, the pressure control passage comprises a pressure tap bore extending generally in the axial direction of the compression mechanism, and wherein: the pressure taking hole comprises a first section connected to the second compression cavity and a second section connected with the first section in the axial direction of the compression mechanism, and the flow cross-sectional area of the first section is smaller than that of the second section, so that a throttling expansion structure is formed at the connection part of the first section and the second section; and/or the liquid discharge control mechanism comprises an expansion hole, a first passage groove and a second passage groove which are arranged in the fixed scroll, the pressure taking hole is connected with the expansion hole through the first passage groove, the expansion hole is connected with the pressure control cavity through the second passage groove, and the flow cross-sectional area of the expansion hole is larger than that of the first passage groove, so that a throttling expansion structure is formed at the connection position of the expansion hole and the first passage groove.

Optionally, the pressure pick-up bore, the expansion bore and the piston bore section are arranged to lie in different planes extending substantially in the axial direction of the compression mechanism.

Optionally, the non-orbiting scroll further has a hub formed on a second side of the non-orbiting scroll end plate opposite to the first side, and the drainage passage and the drainage control mechanism are provided at a position radially outside the hub, or the drainage passage and the drainage control mechanism are provided at a position of the hub.

Optionally, the drainage channels comprise two sets of drainage channels arranged substantially symmetrically on either side of a central axis of the compression mechanism.

Optionally, at least one of the two sets of liquid discharge channels includes a plurality of liquid discharge channels, and the pressure control chamber in each of the plurality of liquid discharge channels is communicated through the communication groove.

Alternatively, in the case where the liquid discharge channel and the liquid discharge control mechanism are provided at the position of the hub, the liquid discharge control mechanism includes a single pressure-taking hole, and the liquid discharge channel includes two sets of liquid discharge channels arranged substantially symmetrically on both sides of the central axis of the compression mechanism, the single pressure-taking hole being provided between the two sets of liquid discharge channels and communicating with the pressure control chambers in the two sets of liquid discharge channels, respectively.

Optionally, a seal is provided between the piston and the piston bore section, which always isolates the liquid outlet from the pressure control chamber in the event of the piston being in any position.

Optionally, the base of the piston bore section is formed with a seal seat engageable with the lower end face of the piston and forming a seal against the liquid entry section.

Optionally, the drainage channel is configured to: when viewed in the axial direction of the compression mechanism, a portion of the liquid intake section overlaps the non-orbiting scroll blade.

Optionally, the liquid discharge control mechanism has a throttling expansion structure adapted to expand and vaporize liquid fluid from within the compression mechanism to create a pressure differential in a passive manner.

Alternatively, the discharge control mechanism uses only fluid from within the compression mechanism to create the pressure differential.

According to another aspect of the present invention, there is also provided a scroll compressor, wherein the scroll compressor comprises a compression mechanism according to the above description.

According to the utility model discloses a compression mechanism and scroll compressor adopt new design, not only can discharge the too much liquid in the compression chamber in time, effectively prevent the liquid of compressor from hitting the damage, especially take liquid operating mode to the start of compressor, can also reduce the start moment of torsion of compressor, prolong the life of motor effectively. Furthermore, according to the utility model discloses a compression mechanism and scroll compressor adopt new flowing back control mechanism, need not to set up the power supply alone, need not to make pressure differential from the outside fluid introduction of compression mechanism, and not only simple structure, spare part are few, the reliability is high, easily production moreover and manufacturing, low cost.

Drawings

Features and advantages of one or more embodiments of the present invention will become more readily understood from the following description with reference to the accompanying drawings, in which:

fig. 1 is an exploded perspective view of a compression mechanism of a scroll compressor according to a first embodiment of the present invention, in which an orbiting scroll is not shown in the drawings;

fig. 2 is an enlarged detail view of a compression mechanism of a scroll compressor according to a first embodiment of the present invention, in which some features of a liquid discharge passage and a liquid discharge control mechanism are particularly shown;

fig. 3a and 3b are longitudinal sectional views of a compression mechanism of a scroll compressor according to a first embodiment of the present invention in a liquid discharge state and in a non-liquid discharge state, respectively;

fig. 4 is a longitudinal sectional view of an additional section of a compression mechanism of a scroll compressor according to a first embodiment of the present invention, showing a pressure tap hole;

fig. 5 is a cross-sectional view of a compression mechanism of a scroll compressor according to a first embodiment of the present invention;

fig. 6 is an exploded perspective view of a compression mechanism of a scroll compressor according to a second embodiment of the present invention, in which an orbiting scroll is not shown in the drawings;

fig. 7 is a plan view of a compression mechanism of a scroll compressor according to a second embodiment of the present invention, with a cover removed in a liquid discharge control mechanism; and

fig. 8 is a longitudinal sectional view of a fixed scroll of a compression mechanism of a scroll compressor according to a second embodiment of the present invention.

Detailed Description

Exemplary embodiments will now be described more fully with reference to the accompanying drawings.

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

The general structure of a scroll compressor, in particular, a compression mechanism of a scroll compressor according to a first embodiment of the present invention is described below with reference to fig. 1. Generally, a scroll compressor includes a compression mechanism, a motor, a rotary shaft, a main bearing housing, and a housing defining an inner space accommodating the above components. The interior space of the housing defines a suction pressure region and a discharge pressure region.

The compression mechanism includes a fixed scroll 100 and an orbiting scroll 200. Orbiting scroll 200 includes an orbiting scroll end plate 20 and an orbiting scroll blade 22 formed at one side of the orbiting scroll end plate. Non-orbiting scroll 100 includes a non-orbiting scroll end plate 10, a non-orbiting scroll blade 12 extending from a first side of the non-orbiting scroll end plate 10, and a hub 14 extending from a second side of the non-orbiting scroll end plate 10 opposite the first side thereof. An exhaust port is formed in the center of the fixed scroll end plate 10, and a boss 14 is provided so as to surround the exhaust port. The non-orbiting scroll blade 12 and the orbiting scroll blade 22 are engageable with each other such that a series of compression chambers including a central compression chamber located at the center of the non-orbiting scroll 100 and communicating with a discharge port at the center of the non-orbiting scroll end plate 10, a suction chamber located radially outside of the non-orbiting scroll 100 and communicating with a suction port of the non-orbiting scroll 100, and a plurality of intermediate compression chambers located between the central compression chamber and the suction chamber CI are formed between the non-orbiting scroll blade 12 and the orbiting scroll blade 22 when the scroll compressor is operated. The motor is configured to rotate a rotation shaft which drives the orbiting scroll 200 to orbit with respect to the non-orbiting scroll 100, and refrigerant fluid enters the compression mechanism from a suction pressure region, is compressed through a series of compression chambers, is discharged from a discharge port at the center of the non-orbiting scroll end plate 10, and is discharged to a discharge pressure region.

To achieve the drainage of the compression mechanism, a drainage land 40 is formed radially outside the hub 14 of the non-orbiting scroll 100, and the drainage land 40 is higher than the second side surface of the non-orbiting scroll end plate 10. A liquid discharge channel is formed at the liquid discharge mechanism platform 40. As shown in fig. 3a and 3b, the liquid discharge passage is configured to extend through the non-orbiting scroll 100 substantially in the axial direction of the compression mechanism. The liquid discharge channel comprises, in the axial direction of the compression mechanism, a piston port section 41 and a liquid inlet section 42. One end of the liquid inlet section 42 is connected to the piston port section 41, and the opposite end of the liquid inlet section 42 is connected to the suction chamber CI. A first end of the piston tunnel section 41 forms an opening in the drainage platform 40 and a second end of the piston tunnel section 41 opposite its first end is connected to the liquid inlet section 42. The side of the piston port section 41 also has a liquid outlet 43 which communicates with the suction pressure region outside the compression mechanism. In order to increase the flow area and allow the liquid to be discharged more smoothly, the liquid outlet 43 may preferably be provided in the form of an elongated slot extending away from the piston port section 41 from the side of the piston port section 41 in a direction tangential to the side wall of the piston port section 41. Further, preferably, the liquid inlet section 42 may be configured to: a portion of the liquid intake section 42 overlaps the non-orbiting scroll blade 12 when viewed in the axial direction of the compression mechanism. By this configuration, on the one hand, the area of the liquid inlet section 42 can be further increased, enabling liquid to enter the drainage channel more quickly, and on the other hand, the design of the location of the drainage channel can be facilitated while ensuring the functionality of the liquid inlet.

The compression mechanism further includes a liquid discharge control mechanism provided at the liquid discharge mechanism platform 40 for controlling the opening and closing of the liquid discharge passage. The discharge control mechanism creates a pressure differential in a passive manner such that the discharge passage selectively provides fluid communication between the suction chamber CI and a suction pressure region external to the compression mechanism through the discharge control mechanism. Herein, "passive" may refer to: the whole liquid discharge control mechanism does not involve any component needing electric power/power, such as a solenoid valve, to form the pressure difference, but automatically uses the fluid from the compression mechanism to form the pressure difference, so as to realize automatic liquid discharge. Referring to fig. 2, the liquid discharge control mechanism mainly includes a piston 31, a cover, a fixing member 34, a pressure-taking hole 45, and an expansion hole 48. The piston 31 is received within the piston bore section 41 of the drain passage and is movable along the piston bore section 41 between an open position and a closed position. Preferably, the lower end face of the piston 31 is configured as a conical, spherical or planar surface, the base of the piston bore section 41 is formed with a sealing seat 44, and the lower end face of the piston 31 is capable of engaging with the sealing seat of the piston bore section 41 and forming a seal against the liquid inlet section 42. It will also be understood by those skilled in the art that the present invention is not limited to the opening and closing of the discharge passage by the piston, but may be implemented by any other means allowing control by a pressure difference, such as an elastic valve plate capable of opening and closing under the action of a pressure difference.

The cover comprises a gasket 32 and a cover plate 33, and the gasket 32 and the cover plate 33 are sequentially mounted and fixed to the drain platform 40 and cover over the piston bore section 41 of the drain passage to form a seal by inserting a fixing member 34, such as a screw, through mounting holes in the cover plate 33 and the gasket 32 in sequence and into the mounting hole at the drain platform 40, thereby forming a pressure control chamber CP in the area between the cover and the piston 31 within the piston bore section 41. By creating a differential pressure by regulating the pressure in the pressure control chamber CP, the piston 31 can be moved to its open or closed position as desired.

Referring to fig. 4, a pressure taking hole 45 is formed in the non-orbiting scroll 100 to extend substantially in the axial direction of the compression mechanism. A first end of the pressure-taking hole 45 is communicated to an intermediate compression chamber on the radially inner side of the suction chamber CI, and a second end of the pressure-taking hole 45 opposite to the first end thereof forms an opening in the drainage mechanism platform 40. Referring to fig. 3a and 3b, the expansion hole 48 is configured as a blind hole formed in the non-orbiting scroll 100 extending substantially in the axial direction of the compression mechanism, and one end of the expansion hole 48 is opened on the drain platform 40. As shown in fig. 2, the pressure taking hole 45, the expansion hole 48, and the opening of the piston bore section 41 of the drain passage formed on the drain mechanism platform 40 are connected in sequence via the first passage groove 47 and the second passage groove 46 formed at the drain mechanism platform 40, whereby the second end of the pressure taking hole 45 indirectly communicates with the pressure control chamber CP. In the first embodiment of the present invention, the first passage groove 47 connects the pressure taking hole 45 and the expansion hole 48, the second passage groove 46 connects the expansion hole 48 and the pressure control chamber CP, and the pressure taking hole 45, the first passage groove 47, the expansion hole 48, and the second passage groove 46 together constitute a pressure control passage for leading the fluid in one intermediate compression chamber of the radial inner side of the suction chamber CI to the pressure control chamber CP.

More specifically, as shown in fig. 2, in the present specification, the "flow cross-sectional area" refers to an area of a cross section perpendicular to the flow direction of the fluid, and the flow cross-sectional area of the expansion hole 45 is significantly increased compared to the flow cross-sectional area of the first passage groove 47. In other words, the pressure control passage forms a throttle expansion structure at the junction from the first passage groove 47 and the expansion hole 45.

As shown in fig. 4, the pressure-taking hole 45 also has a throttle expansion structure. Specifically, the pressure taking hole 45 includes a first section 451 having a first end and a second section 452 having a second end in the flow direction of the fluid (in the axial direction of the compression mechanism in the present embodiment), and the first section 451 and the second section 452 are connected to each other, and a throttle expansion structure in which the flow cross-sectional area abruptly increases is formed at the connection of the two. That is, the cross-sectional flow area of the second section 452 is substantially greater than the cross-sectional flow area of the first section 451.

The operation of the liquid discharge control mechanism of the scroll compressor will now be described with reference to fig. 3a and 3 b. When there is too much liquid in the compression chambers of a scroll compressor to require drainage, the compression chambers, including the suction chamber CI, are filled with liquid at equal pressure due to the incompressibility of the liquid, as shown in figure 3a. The liquid in the suction chamber CI is pushed and pressed by the scroll blades into the liquid inlet section 42 and contacts the lower end surface of the piston 31, applying a thrust to the lower end surface of the piston 31. While the liquid of the middle compression chamber radially inside the suction chamber CI enters the pressure taking hole 45, since the flow cross-sectional area of the first section 451 of the pressure taking hole 45 is much smaller than that of the second section 452, the liquid is converted into a gas or gas-liquid mixture and reduced in pressure due to the sudden expansion of the volume when passing through the junction of the first section 451 and the second section 452, and the gas or gas-liquid mixture further vaporizes and reduced in pressure due to the sudden expansion of the volume again when entering the expansion hole 48 via the first passage groove 47, and finally enters the pressure control chamber CP via the second passage groove 46. Therefore, the pressure applied to the upper end surface of the piston 31 by the fluid entering the pressure control chamber CP is much smaller than the liquid thrust force experienced by the lower end surface of the piston 31, the piston 31 moves upward to its open position under the action of the pressure difference, the lower end surface of the piston 31 separates from the seal seat 44 of the base of the piston port section 41, and the liquid in the suction chamber CI is discharged to the outside of the compression mechanism through the liquid inlet section 42, the piston port section 41, and the liquid outlet 43 in this order.

When the scroll compressor does not require liquid discharge, the compression chambers, including the suction chamber CI, are normally filled with gaseous working medium, as shown in fig. 3 b. The pressure of the working medium increases gradually from the radially outer to the radially inner compression chambers through compression in the series of compression chambers, i.e., the pressure in the compression chambers closer to the radially outer side is lower than the pressure in the compression chambers closer to the radially inner side in a normal operating state of the compressor. The higher pressure gas in the middle compression cavity at the radial inner side of the air suction cavity CI enters the pressure control cavity CP through a pressure control channel formed by a pressure taking hole 45, a passage groove and the like, and although a throttling expansion structure is arranged in the pressure control channel, the pressure of the gas entering the pressure control cavity CP is slightly reduced compared with the pressure of the gas in the middle compression cavity at the radial inner side of the air suction cavity CI, but is still higher than the pressure in the air suction cavity CI. Thus, the lower end face of the piston 31 is subjected to a lower pressure than the upper end face of the piston 31, the piston 31 moves downwardly to its closed position under the action of the pressure differential, the lower end face of the piston 31 engages the sealing seat 44 of the base of the piston port section 41 and seals the liquid intake section 42, thereby isolating the suction chamber CI from the suction pressure region outside the compression mechanism, and the scroll compressor is capable of normal compression operation.

Although in the embodiments of the present invention, the liquid discharge channel is preferably configured to communicate with the suction chamber CI so that the liquid can be discharged from the compression mechanism as soon as possible, it will be understood by those skilled in the art that the liquid discharge channel may also be configured to communicate with an intermediate compression chamber of the plurality of intermediate compression chambers, which is close to the suction chamber CI. In addition, in the embodiment of the present invention, the pressure taking hole 45 is preferably configured to be capable of communicating with the central compression chamber or the intermediate compression chamber close to the central compression chamber so as to ensure that the fluid pressure drained to the pressure control chamber CP is higher, but it can be understood by those skilled in the art that the control of the piston can be realized as long as the compression chamber communicated with the pressure taking hole 45 is closer to the radial inner side of the compression mechanism than the compression chamber communicated with the liquid discharge passage, that is, the pressure in the compression chamber communicated with the pressure taking hole 45 is higher than the pressure in the compression chamber communicated with the liquid discharge passage.

As shown in fig. 5, the liquid inlet section 42 and the pressure taking hole 45 are respectively communicated to different first compression chamber C1 and second compression chamber C2, and the first compression chamber C1 is closer to the radial outer side of the compression mechanism than the second compression chamber C2. Therefore, the pressure in the pressure control cavity CP can be ensured to be constantly higher than the pressure in the liquid inlet section 42 under the non-liquid impact working condition, so that the piston 31 is ensured to be in the closed position, and the compressor can normally run. Under the liquid impact working condition, the liquid discharge channel can provide fluid communication between the first compression chamber C1 and the suction pressure area outside the compression mechanism, and liquid in the compression chamber can be discharged to the outside of the compression mechanism in time without experiencing or experiencing the pushing and squeezing of the scroll blades as little as possible, so that the impact of the liquid on the scroll blades is reduced, and the damage of the scroll blades is avoided. At the initial stage of starting the compressor which is particularly easy to generate liquid impact, the starting torque of the compressor is reduced, the impact load of the motor is reduced, the working stability and reliability of the compressor are ensured, and the service life of the motor is effectively prolonged. Furthermore, it is obvious that the liquid discharge control mechanism according to the present invention includes a throttle expansion structure provided in the pressure control passage, the throttle expansion structure being adapted to expand and gasify the liquid fluid from inside the compression mechanism to create a pressure difference in a passive manner, so that control of opening and closing of the liquid discharge passage can be achieved without separate electric/power source, and therefore, the parts are fewer, the production is simple and easy, and the cost is low. Furthermore, according to the utility model discloses a flowing back control mechanism only utilizes the fluid that comes from the compression mechanism in to make the pressure differential, and need not to introduce the fluid from the compression mechanism outside, and the structure is simpler, the operation is probably reliable.

Furthermore, in order to allow the liquid in the suction chamber CI to be discharged through the liquid discharge channel more quickly during liquid discharge, it is preferable that the side wall of the piston 31 does not cover the liquid outlet 43 when the piston 31 is in its open position, thereby increasing the flow area of the liquid discharge channel so that the liquid can flow out more smoothly through the liquid outlet 43.

In addition, in order to ensure effective control of the pressure control chamber CP, it is preferable that a sealing member 312, such as an O-ring, is further provided between the piston 31 and the piston bore section 41, and the sealing member 312 is received in a sealing groove 311 formed in an outer side surface of the piston 31 to provide sealing between the outer side surface of the piston 31 and an inner side surface of the piston bore section 41. In addition, no matter the piston 31 is in any position, the sealing member 312 is always located above the liquid outlet 43, so that the space above the sealing member 312 is always sealed and isolated from the space below, the liquid outlet 43 is also isolated from the pressure control cavity CP, liquid is prevented from entering the pressure control cavity CP, and accurate and quick control of the pressure control cavity CP on the piston 31 is guaranteed.

Further, although the pressure control passage shown in the first embodiment of the present invention includes the expansion hole 48, it can be understood by those skilled in the art that the expansion hole 48 may be omitted and the pressure taking hole 45 may be directly connected to the pressure control chamber CP through the passage groove as long as the pressure control passage has the throttle expansion structure. In the case where the expansion hole 48 is omitted, the throttle expansion structure may be formed, for example, by providing the first section 451 and the second section 452 different in flow cross section through the pressure taking hole 45 as described above, or may be formed, for example, by making the flow cross-sectional area of the passage groove much larger than the flow cross-sectional area of the pressure taking hole 45. In addition, it will be understood by those skilled in the art that the pressure control passage may include one or more throttle expansion structures, i.e., an expansion hole 48 having a significantly increased flow cross-sectional area compared to the first passage groove 47, a pressure take-off hole 45 having an abruptly increased flow cross-sectional area, and a passage groove having an abruptly increased flow cross-sectional area compared to the pressure take-off hole 45 may be provided in the pressure control passage, individually or in combination.

Furthermore, in order to make the liquid discharge control mechanism more compact, space-saving, and easier to machine, it is preferable that the pressure taking hole 45, the expansion hole 48, and the piston tunnel section 41 be arranged so as to each extend in the axial direction of the compression mechanism and lie in different planes (not coplanar) extending in the axial direction of the compression mechanism. The first and second passage grooves 47 and 46 are formed by notching the upper surface of the drainage mechanism platform 40, and for one set of drainage channels, a single cover can be used to cover and seal over the pressure tapping hole 45, the expansion hole 48, the drainage channel, the first and second passage grooves 47 and 46 at the same time, thereby making the mechanism less in parts, less in occupied space, and simpler to produce and assemble.

On the other hand, it will be understood by those skilled in the art that the pressure tapping hole 45 may be separately arranged from the liquid discharge passage and a plurality of covers may be used to cover and seal the pressure tapping hole 45 and the piston bore section 41 of the liquid discharge passage to provide a more flexible design of the component positions. Even further, the pressure taking hole 45 may be disposed radially inward of the hub 14 to introduce high-pressure gas of a central compression chamber or a discharge chamber into the pressure control chamber CP. Further, the pressure taking hole 45 is not limited to extending in the axial direction of the compression mechanism as shown in fig. 4, but may be configured in other suitable configurations, such as a bent configuration or an inclined configuration extending obliquely to the horizontal direction in the non-orbiting scroll end plate, as long as the first end of the pressure taking hole 45 communicates with the second compression chamber and the second end of the pressure taking hole 45 can directly or indirectly communicate with the pressure control chamber CP. For example, under the condition that the pressure tapping hole is in a bending structure formed by connecting a section extending along the axial direction and a section extending along the transverse direction, the section extending along the axial direction of the pressure tapping hole is provided with a first end communicated with the second compression cavity, the section extending along the transverse direction of the pressure tapping hole is formed in the fixed scroll end plate and is provided with a second end, the second end of the pressure tapping hole can be directly connected to the pressure control cavity CP without arranging a covering piece to cover and seal the pressure tapping hole, as long as the pressure tapping hole is provided with a throttling expansion structure, the purpose that liquid in the compression cavity is timely discharged to the outside of the compression mechanism under the liquid discharge working condition can be achieved, and the compressor can normally run under the non-liquid impact working condition is guaranteed.

It will be appreciated by those skilled in the art that a plurality of drainage channels and drainage control mechanisms may be provided at a plurality of locations on the non-orbiting scroll depending on the drainage requirements. The drainage channel and the drainage control mechanism may be provided radially outside the hub of the fixed scroll as in the first embodiment of the present invention, or may be provided on the end surface of the hub of the fixed scroll. A scroll compressor according to a second embodiment of the present invention, in which a liquid discharge passage and a liquid discharge control mechanism are provided on an end surface of the boss portion 14 of the fixed scroll, will be described below with reference to fig. 6 to 8. In this second embodiment, the main components, mounting manner, and operation principle of the scroll compressor, particularly the liquid discharge operation and principle, are similar to those of the first embodiment of the present disclosure, and thus, detailed description thereof is omitted.

As shown in fig. 6, the upper end surface of the boss portion 14a of the non-orbiting scroll 100a forms a discharge mechanism land 40a. The liquid discharge mechanism platform 40 is formed with a liquid discharge channel and a liquid discharge control mechanism. As shown in fig. 8, the drainage passage is configured to extend through the non-orbiting scroll 100a from the upper end surface of the boss portion 14a to the first side of the non-orbiting scroll end plate 10a substantially in the axial direction of the compression mechanism. With the first embodiment of the present invention, the liquid discharge passage includes the interconnected piston duct section 41a and the liquid inlet section 42a in the axial direction of the compression mechanism, the one end of the liquid inlet section 42a communicates with the first compression chamber in the series of compression chambers of the compression mechanism, and the side portion of the piston duct section 41a further has the liquid outlet 43a communicating with the suction pressure region outside the compression mechanism.

Referring to fig. 6, the liquid discharge control mechanism mainly includes a piston 31a, a cover, a fixing member 34a, and a pressure-taking hole 45a. The piston 31a is received within the piston bore section 41a of the drain passage and is movable along the piston bore section 41a between an open position and a closed position. The cover includes a gasket 32a and a cover plate 33a, both of which form a seal by mounting and fixing a fixing member 34a such as a screw to the drain mechanism platform 40a in turn and covering over the piston bore section 41a of the drain passage, thereby forming a pressure control chamber in the area between the cover and the piston 31a within the piston bore section 41 a. Referring to fig. 8, the pressure taking hole 45a is configured to extend through the non-orbiting scroll 100a from the upper end surface of the boss portion 14a to the first side of the non-orbiting scroll end plate 10a substantially in the axial direction of the compression mechanism. A first end of the pressure taking hole 45a communicates with a second compression chamber radially inside the first compression chamber, and a second end of the pressure taking hole 45 opposite to the first end thereof communicates with a pressure control chamber in the piston port section 41a through a passage groove 47 a. The passage groove 47a is formed by making a groove in the upper end surface of the boss portion 14 a. The pressure-taking hole 45 and the passage groove 47a together constitute a pressure control passage for introducing the fluid in the second compression chamber to the pressure control chamber CP. Similar to the first embodiment, the pressure control passage also has one or more throttle expansion structures, for example, as shown in fig. 8, the pressure taking hole 45a includes a first section 451a having a first end and a second section 452a having a second end in the axial direction of the compression mechanism, the first section 451a and the second section 452a are connected to each other, and a throttle expansion structure in which the flow cross-sectional area increases abruptly is formed at the connection of the two.

Preferably, as shown in fig. 7, the non-orbiting scroll 100a may form two sets of drainage channels arranged substantially symmetrically on both sides of the non-orbiting scroll axis, so that the compression mechanism is balanced in drainage. In addition, each set of drainage channels may include one or more drainage channels, with one piston 31a disposed in the piston bore 41a in each drainage channel. The upper end surface of the boss portion 14a of the non-orbiting scroll 100a is also recessed to form a communication groove 48a to communicate the pressure control chambers in each set of the liquid discharge passages. The design of the piston pore passages and the pistons further increases the flow area of the liquid discharge channel, so that the liquid can be discharged out of the compression mechanism as soon as possible.

Preferably, the cover is configured to have substantially the same shape as the upper end surface of the hub portion 14a of the non-orbiting scroll 100a, and as shown in fig. 6, the cover is configured to have a single annular shape. A single annular cover member can simultaneously cover and seal over the pressure tapping hole 45a, the liquid discharge channel and passage groove 47a and the communication groove 48a, thereby making the mechanism less in parts, less in space, and simpler to produce and assemble. Further, only one pressure-taking hole 45a may be provided between the two sets of liquid discharge passages. Because the pressure control chamber in all piston pore channel sections 41a in every group of drainage channels is communicated by the communicating groove 48a, and every group of drainage channels is communicated with the pressure taking hole 45a through the passage groove 47a, and for the whole compression mechanism, only a single pressure taking hole 45a needs to be arranged, so that the synchronous control of a plurality of pistons can be realized, the structure is simpler, the drainage is quicker, and the processing is easier. Preferably, a single pressure pick-up hole 45a is provided at approximately the middle of the two sets of drainage channels to enable substantially equal fluid flow from the compression chambers into the pressure control chambers.

Furthermore, compared with the first embodiment of the present invention, since the liquid discharge channel and the liquid discharge control mechanism are provided in the liquid discharge mechanism platform 40a formed by the upper end surface of the boss 14a of the fixed scroll 100a in the second embodiment of the present invention, the liquid discharge mechanism platform does not need to be processed separately, and not only the processing and the production are more convenient, but also the space is saved more.

Furthermore, although the liquid discharge channel and the liquid discharge control mechanism are provided in the fixed scroll in the embodiment of the present invention, those skilled in the art can understand that the liquid discharge channel and the liquid discharge control mechanism may be provided in the movable scroll and obtain similar effects.

While the present invention has been described with reference to exemplary embodiments, it is to be understood that the invention is not limited to the precise embodiments described and illustrated herein, and that various changes may be made therein by those skilled in the art without departing from the scope of the invention as defined in the appended claims. It should also be understood that features of the various embodiments may be combined with each other or may be omitted without departing from the scope of the claims.

Claims (18)

1. A compression mechanism comprising:

an orbiting scroll having an orbiting scroll end plate and an orbiting scroll blade formed at one side of the orbiting scroll end plate;

a non-orbiting scroll having a non-orbiting scroll end plate and a non-orbiting scroll blade formed on a first side of the non-orbiting scroll end plate, the orbiting and non-orbiting scroll blades engaging each other to form a series of compression chambers between the orbiting and non-orbiting scrolls;

characterized in that the compression mechanism is provided with a liquid discharge channel and a liquid discharge control mechanism adapted to create a pressure differential in a passive manner such that the liquid discharge channel is capable of selectively providing fluid communication between a first compression chamber of the series of compression chambers and an exterior of the compression mechanism.

2. The compression mechanism of claim 1, wherein the drain control mechanism includes a piston disposed within the drain passage and movable under the pressure differential between an open position providing the fluid communication and a closed position not providing the fluid communication.

3. The compression mechanism as claimed in claim 2, wherein the drainage passage is provided in the non-orbiting scroll and is configured to extend through the non-orbiting scroll substantially in an axial direction of the compression mechanism, the drainage passage including a piston port section accommodating the piston and a liquid inlet section communicating the piston port section with the first compression chamber, a side of the piston port section having a liquid outlet communicating with an outside of the compression mechanism.

4. The compression mechanism of claim 3, further comprising a cover covering and sealing the piston bore segment such that a pressure control chamber is formed within the piston bore segment in an area between the cover and the piston.

5. The compression mechanism as claimed in claim 4, wherein the liquid discharge control mechanism further includes a pressure control passage provided in the non-orbiting scroll, one end of the pressure control passage being communicated to a second compression chamber of the series of compression chambers, the other end of the pressure control passage being communicated to the pressure control chamber, the first compression chamber being closer to a radially outer side of the compression mechanism than the second compression chamber, and the pressure control passage having a throttle expansion structure.

6. A compression mechanism as claimed in claim 5, wherein said first compression chamber is a suction chamber of said series or an intermediate compression chamber adjacent said suction chamber.

7. The compression mechanism of claim 5, wherein the pressure control passage includes a pressure tap hole extending generally in the axial direction of the compression mechanism, and wherein:

the pressure taking hole comprises a first section connected to the second compression cavity and a second section connected with the first section in the axial direction of the compression mechanism, and the flow cross-sectional area of the first section is smaller than that of the second section, so that the throttling expansion structure is formed at the connection position of the first section and the second section; and/or

The liquid discharge control mechanism comprises an expansion hole, a first passage groove and a second passage groove, wherein the expansion hole, the first passage groove and the second passage groove are arranged in the fixed scroll, the pressure taking hole is connected with the expansion hole through the first passage groove, the expansion hole is connected with the pressure control cavity through the second passage groove, the flow cross-sectional area of the expansion hole is larger than that of the first passage groove, and therefore the throttling expansion structure is formed at the connecting position of the expansion hole and the first passage groove.

8. The compression mechanism of claim 7, wherein the take-up port, the expansion port, and the piston tunnel segment are arranged to lie in different planes that extend generally in an axial direction of the compression mechanism.

9. The compression mechanism according to any one of claims 1 to 8, wherein:

the non-orbiting scroll further has a boss portion formed at a second side of the non-orbiting scroll end plate opposite to the first side, and

the drain passage and the drain control mechanism are provided at a position radially outside the hub, or the drain passage and the drain control mechanism are provided at a position of the hub.

10. The compression mechanism of any one of claims 4 to 8, wherein the drainage channels comprise two sets of drainage channels arranged substantially symmetrically on either side of a central axis of the compression mechanism.

11. The compression mechanism of claim 10, wherein at least one of the two sets of drainage channels comprises a plurality of drainage channels, the pressure control chamber in each of the plurality of drainage channels being in communication with the communication channel.

12. The compression mechanism of claim 9, wherein, with the drainage channel and the drainage control mechanism provided at the location of the hub, the drainage control mechanism includes a single pressure-tapping hole, and wherein the drainage channel includes two sets of drainage channels arranged substantially symmetrically on either side of a central axis of the compression mechanism, the single pressure-tapping hole being provided between the two sets of drainage channels and communicating with the pressure control chambers within the two sets of drainage channels, respectively.

13. A compression mechanism according to any one of claims 4 to 8, wherein a seal is provided between the piston and the piston port section, which seal always seals the liquid outlet from the pressure control chamber with the piston in any position.

14. A compression mechanism as claimed in any one of claims 3 to 8, wherein the base of the piston bore section is formed with a sealing seat engageable with the lower end face of the piston and forming a seal against the liquid inlet section.

15. The compression mechanism of any one of claims 3-8, wherein the drainage channel is configured to: a portion of the liquid intake section overlaps with the non-orbiting scroll blade when viewed in an axial direction of the compression mechanism.

16. A compression mechanism as claimed in any one of claims 1 to 4, wherein the liquid discharge control mechanism has a throttled expansion structure adapted to expand liquid fluid from within the compression mechanism to vaporise to create a pressure differential in a passive manner.

17. The compression mechanism of any one of claims 1-8, wherein the liquid discharge control mechanism creates a pressure differential using only fluid from within the compression mechanism.

18. A scroll compressor, characterized by comprising the compression mechanism according to any one of claims 1 to 17.

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