CN113833659B - Scroll compression mechanism and scroll compressor - Google Patents
Scroll compression mechanism and scroll compressor Download PDFInfo
- Publication number
- CN113833659B CN113833659B CN202010579961.8A CN202010579961A CN113833659B CN 113833659 B CN113833659 B CN 113833659B CN 202010579961 A CN202010579961 A CN 202010579961A CN 113833659 B CN113833659 B CN 113833659B
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- Prior art keywords
- oil supply
- compression mechanism
- scroll
- pressure
- transverse
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- 230000006835 compression Effects 0.000 title claims abstract description 107
- 238000007906 compression Methods 0.000 title claims abstract description 107
- 230000007246 mechanism Effects 0.000 title claims abstract description 97
- 239000003921 oil Substances 0.000 claims abstract description 200
- 239000012530 fluid Substances 0.000 claims abstract description 72
- 239000010687 lubricating oil Substances 0.000 claims abstract description 18
- 230000001105 regulatory effect Effects 0.000 claims abstract description 15
- 239000000314 lubricant Substances 0.000 description 29
- 238000002347 injection Methods 0.000 description 20
- 239000007924 injection Substances 0.000 description 20
- 238000005461 lubrication Methods 0.000 description 19
- 238000004891 communication Methods 0.000 description 14
- 230000008859 change Effects 0.000 description 10
- 230000000052 comparative effect Effects 0.000 description 10
- 238000001704 evaporation Methods 0.000 description 5
- 230000002093 peripheral effect Effects 0.000 description 5
- 238000013461 design Methods 0.000 description 4
- 230000004308 accommodation Effects 0.000 description 3
- 238000005192 partition Methods 0.000 description 3
- 238000009825 accumulation Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 239000010725 compressor oil Substances 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000003595 mist Substances 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/021—Control systems for the circulation of the lubricant
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
本发明涉及涡旋压缩机构和具有其的涡旋压缩机。压缩机构包括：定涡旋部件和动涡旋部件以及将润滑油从润滑油源供应至涡旋压缩机构内的供油通道，压缩机构还包括调节阀和流体压力通道，调节阀包括可动阀体，流体压力通道的第一端与第一压力源流体连通以将第一压力施加于可动阀体的第一侧端，流体压力通道的第二端与第二压力源流体连通以将第二压力施加于可动阀体的第二侧端，使得可动阀体能够基于压差而选择性地朝向减小或增大供油通道的流通横截面积的第一方向或相反的第二方向移动。本发明的涡旋压缩机构和具有其的涡旋压缩机能够根据工况动态地调节供油量和油循环率，同时确保压缩机的工作可靠性和压缩机所应用的系统的工作性能。
The present invention relates to a scroll compression mechanism and a scroll compressor having the same. The compression mechanism includes: a fixed scroll component and a movable scroll component and an oil supply channel for supplying lubricating oil from a lubricating oil source to the scroll compression mechanism. The compression mechanism also includes a regulating valve and a fluid pressure channel. The regulating valve includes a movable valve body. The first end of the fluid pressure channel is fluidly connected to a first pressure source to apply a first pressure to a first side end of the movable valve body. The second end of the fluid pressure channel is fluidly connected to a second pressure source to apply a second pressure to a second side end of the movable valve body, so that the movable valve body can selectively move toward a first direction or an opposite second direction to reduce or increase the flow cross-sectional area of the oil supply channel based on a pressure difference. The scroll compression mechanism of the present invention and the scroll compressor having the same can dynamically adjust the oil supply amount and the oil circulation rate according to the working conditions, while ensuring the working reliability of the compressor and the working performance of the system to which the compressor is applied.
Description
Technical Field
The present invention relates to a scroll compressor, and more particularly, to a scroll compressor having improvements in dynamic adjustment of oil amount of a scroll compression mechanism.
Background
Compressors, such as scroll compressors, are used in refrigeration (freezing or refrigerating) systems, air conditioning systems, and heat pump systems. Scroll compressors include a compression mechanism for compressing a working fluid, such as a refrigerant, which in turn includes an orbiting scroll member and a non-orbiting scroll member. When the scroll compressor is operated, there is a relative movement between the movable scroll member and the fixed scroll member of the compression mechanism. In order to reduce wear and power consumption, it is necessary to provide lubrication (such as supply of lubricating oil) to the compression mechanism to improve friction between the orbiting scroll member and the non-orbiting scroll member, while the generated oil film also improves the sealability of the compression mechanism to improve volumetric efficiency, and the like.
Typically, the oil circulation rate is used to characterize how much lubrication oil is carried by the working fluid, and accordingly the degree to which lubrication oil is supplied to the compression mechanism. Too much or too little supply of lubricating oil can adversely affect the normal operation of the compression mechanism itself, the performance energy efficiency of the system, and the like. Excessive oil circulation rates can reduce the heat transfer efficiency of the system and can also cause lubrication oil to accumulate around (especially above) the discharge valve assembly (e.g., HVE valve assembly) at the discharge port and discharge recess of the non-orbiting scroll member causing certain problems with the scroll compressor (e.g., operational stability problems of the discharge valve assembly and/or discharge reliability problems of the compression mechanism).
The prior art provides a compression mechanism oil supply configuration that enables oil circulation rates to be within a suitable range at different compressor speeds and/or different system operating parameters. However, the oil supply structure in the prior art cannot adjust the oil injection amount or the oil circulation rate according to the change of the working condition so as to meet the requirements of performance energy efficiency or stability and reliability of the compressor under different working conditions, for example, under the working conditions of rated load or light load, too much oil injection leads to too large oil circulation rate, thereby reducing the heat exchange efficiency of the system and leading to the problem of discharge stability and reliability caused by accumulation of lubricating oil, while under severe working conditions of high load (such as high rotating speed) or high temperature, too little oil injection leads to insufficient lubrication of the compression mechanism, thereby increasing abrasion and reducing power consumption, and further reducing the stability and reliability of the operation of the compressor.
Accordingly, there is a need for a compressor oil supply configuration that can dynamically adjust the amount of oil injected based on operating conditions.
Here, it should be noted that the technical content provided in this section is intended to facilitate understanding of the present invention by those skilled in the art, and does not necessarily constitute prior art.
Disclosure of Invention
The full appreciation of the invention is not gained by taking the entire specification, but rather the entire specification, claims, drawings, and abstract as a whole.
An object of the present invention is to provide a scroll compression mechanism capable of dynamically adjusting the amount of fuel injected according to the operating conditions.
In order to achieve the above objects, the present invention provides a scroll compression mechanism comprising a fixed scroll member and an orbiting scroll member comprising an orbiting scroll end plate, the orbiting scroll member and the fixed scroll member cooperating to define a series of working fluid pockets including a central compression pocket and a fluid suction pocket, and an oil supply passage for supplying lubricating oil from a source of lubricating oil into the scroll compression mechanism, the scroll compression mechanism further comprising a regulating valve including a movable valve body, and a fluid pressure passage including a first end and a second end, wherein the first end is in fluid communication with a first pressure source for applying a first pressure to a first side end of the movable valve body and the second end is in fluid communication with a second pressure source for applying a second pressure to a second side end of the movable valve body, such that the movable valve body is selectively movable in a first direction of decreasing the cross-sectional flow area of the passage and in a second direction of increasing the cross-sectional area of the passage based on a pressure difference of the first pressure and the second pressure, whereby the scroll compression mechanism is movable in a direction opposite to the first direction of flow of the regulating oil supply.
Advantageously, the oil supply passage, the regulating valve and the fluid pressure passage are provided in the orbiting scroll end plate.
Advantageously, the oil supply passage comprises a vertical oil supply duct substantially parallel to the central axis of the scroll compression mechanism, the vertical oil supply duct opening into the fluid suction chamber, and the movable valve body is partially disposed in the vertical oil supply duct so as to adjust the flow cross-sectional area of the oil supply passage by adjusting the flow cross-sectional area of the vertical oil supply duct.
Advantageously, the oil supply channel further comprises a transverse oil supply duct substantially perpendicular to the central axis, the transverse oil supply duct communicating crosswise with the vertical oil supply duct.
Advantageously, the fluid pressure passage comprises a transverse fluid pressure port substantially perpendicular to the central axis, and the transverse fluid pressure port and the transverse oil supply port are arranged horizontally or vertically in the orbiting scroll end plate.
Advantageously, the transverse fluid pressure duct and the vertical oil supply duct partially overlap in a vertical direction parallel to the central axis, the transverse oil supply duct comprising a main transverse oil supply duct arranged side by side with the transverse fluid pressure duct in case of a horizontal arrangement of the transverse fluid pressure duct and a secondary transverse oil supply duct in intersecting communication with both the main transverse oil supply duct and the vertical oil supply duct, the transverse oil supply duct being arranged side by side with the transverse fluid pressure duct in case of a vertical arrangement of the transverse fluid pressure duct and the transverse oil supply duct.
Advantageously, the orbiting scroll member includes a hub, a base region in an inner space of the hub adjacent to the orbiting scroll end plate serving as the lubricating oil source, an oil inlet end of the oil supply passage being connected to the base region.
Advantageously, the first pressure varies with a change in the operating condition of the scroll compression mechanism or with a change in the operating condition of a system to which the scroll compression mechanism is applied, and/or the second pressure varies with a change in the operating condition of the scroll compression mechanism or with a change in the operating condition of a system to which the scroll compression mechanism is applied.
Advantageously, the regulator valve further comprises a resilient member arranged to be able to abut the second lateral end, the resilient member being adapted to bias the movable valve body towards the first direction.
Advantageously, the first pressure source is the central compression chamber and/or the second pressure source is the fluid suction chamber or a low pressure region located outside the scroll compression mechanism.
Advantageously, the movable valve body comprises a connecting section connecting the first side end and the second side end, the connecting section having a diameter smaller than the diameter of the first side end and smaller than the diameter of the second side end, and the regulator valve is arranged such that, when the movable valve body is moved in the first direction, the connecting section occupies less in the oil supply passage to reduce the flow cross-sectional area of the oil supply passage, and when the movable valve body is moved in the second direction, the connecting section occupies more in the oil supply passage to increase the flow cross-sectional area of the oil supply passage.
The invention also provides a scroll compressor which comprises the scroll compression mechanism.
Therefore, compared with a compressor without an oil supply structure, the scroll compression mechanism with the oil supply structure can realize relatively higher oil circulation rate by adjusting the oil injection quantity of the compressor under severe working conditions according to pressure difference on the premise of not changing the oil circulation rate of rated working conditions, so that the reliability of the compressor is improved, compared with a traditional oil injection device without a regulating valve, the oil injection quantity or the oil circulation rate can be reduced under rated or light-load working conditions, the energy efficiency (such as heat exchange efficiency) in a system applied by the compressor is improved, the problems of discharge stability and reliability caused by accumulation of lubricating oil at an exhaust port of the compression mechanism are avoided, and under the severe working conditions of high temperature and high load, the appropriately large oil injection quantity or the oil circulation rate can be obtained, so that the sufficient lubrication of the compression mechanism is ensured, and the operation reliability of the compressor is improved. That is, since the oil supply structure according to the present invention is provided with the regulating valve that regulates based on the differential pressure that dynamically changes with the change of the operating condition, the oil supply amount can be dynamically regulated to dynamically change the oil circulation rate to match the ideal oil circulation rate under each operating condition.
Drawings
The features and advantages of one or more embodiments of the invention will become more readily apparent from the following description with reference to the accompanying drawings, in which:
fig. 1 is a longitudinal sectional view showing a scroll compressor having a compression mechanism with an oil supply configuration of a comparative example.
Fig. 2 is a longitudinal sectional view showing an orbiting scroll member incorporating a compression mechanism with an oil supply structure of a comparative example.
Fig. 3 is a longitudinal cross-sectional view showing one embodiment of a scroll compression mechanism according to the present invention.
Fig. 4 is a transverse cross-sectional view showing another embodiment of a scroll compression mechanism according to the present invention.
Detailed Description
The invention is described in detail below with the aid of exemplary embodiments with reference to the accompanying drawings. The following detailed description of the invention is merely illustrative of the invention and is in no way intended to limit the invention, its application, or uses.
First, referring to fig. 1 and 2, fig. 1 schematically depicts a longitudinal sectional view of a scroll compressor having a compression mechanism with an oil supply structure CO of a comparative example. Fig. 2 is a longitudinal sectional view showing an orbiting scroll member incorporating a compression mechanism with an oil supply structure of a comparative example.
As shown in fig. 1, scroll compressor 100 includes a housing 110. The housing 110 includes a housing body 112 having a substantially cylindrical shape, a top cover 114 mounted to a top of the housing body 112, and a bottom cover 116 mounted to a bottom of the housing body 112. The housing 110 defines an interior volume IV of the scroll compressor 100. In addition, a partition 119 is provided within the housing 110 such that the partition 119 defines a high pressure region (i.e., a discharge pressure region HR adapted to temporarily store high pressure working fluid to be discharged to the outside of the compressor) with the top cover 114, and the partition 119 defines a low pressure region LR with the housing body 112 and the bottom cover 116. In addition, lubricant of the lubricating oil is stored in an oil pool OR at the bottom of the internal volume IV within the housing 110. In the illustrated example, the scroll compressor is a so-called low-pressure side scroll compressor.
The scroll compressor 100 also includes a suction fitting 194. In the illustrated example, the scroll compressor 100 employs a mid-intake design, i.e., the suction fitting 194 is disposed at a location generally aligned with the main bearing housing 180 in the compressor axial direction. Thereby, the low-temperature and low-pressure working fluid evaporated by the evaporator is sucked into the scroll compressor 100 through the suction fitting 194 to be compressed.
The scroll compressor 100 also includes a drive mechanism 130. The drive mechanism 130 includes an electric motor 132 and a drive shaft 134. The electric motor 132 includes a stator 137 and a rotor 138. The stator 137 is fixedly connected to the inner peripheral wall surface of the housing body 112, and the rotor 138 is fixedly fitted over the drive shaft 134 to integrally rotate with the drive shaft 134. An eccentric pin 139 is provided at the tip end portion of the drive shaft 134.
The scroll compressor 100 also includes a main bearing housing 180. The main bearing housing 180 is fixedly coupled to an inner peripheral wall surface of the housing body 112. Main bearing housing 180 is fixedly connected to the inner peripheral wall surface of housing body 112 by a plurality of circumferentially spaced radial projections thereof such that a plurality of main bearing housing passages PG are formed between main bearing housing 180 and the inner peripheral wall surface of housing body 112 (i.e., between adjacent radial projections of main bearing housing 180) to allow passage of low pressure working fluid drawn into interior volume IV. The main bearing housing 180 supports a portion of the drive shaft 134 via a main bearing 182 provided in the main bearing housing 180.
The scroll compressor 100 also includes a compression mechanism CM adapted to compress a working fluid, such as a refrigerant. The compression mechanism CM includes an orbiting scroll member 150 and a non-orbiting scroll member 160.
The orbiting scroll member 150 includes an end plate 152, a spiral orbiting wrap 154 extending upward from a radially central portion of an upper surface of the end plate 152, and a hub portion 156 extending downward from a radially central portion of a lower surface of the end plate 152. The orbiting scroll member 150 is disposed in a main bearing housing 180 and is axially supported by the main bearing housing 180 so as to be capable of orbiting. Eccentric pin 139 is drivingly coupled to (inserted into) hub 156 (via unloading bushing 190 and/or drive bearing).
The fixed scroll 160 includes an end plate 162, a spiral fixed wrap 164 extending downward from a lower surface of the end plate 162, a discharge port 166 formed at a substantial center of the end plate 162 and adapted to communicate with a central compression chamber ZC of the compression mechanism CM, and a recess 168 formed at a substantial center of the end plate 162, the recess 168 being located above the discharge port 166 and adapted to communicate with a discharge pressure region HR. A discharge valve assembly (such as an HVE valve assembly) 192 is provided in the recess 168 to control the discharge of the compression mechanism CM. In the illustrated example, the fixed scroll 164 includes a radially outermost (annular) outer wall, and a compression mechanism suction window SW is provided in the outer wall at an appropriate circumferential position, the suction window SW allowing low-pressure working fluid to be sucked into the compression mechanism CM, wherein the suction window SW defines a suction pressure area SP.
Fixed scroll 164 is adapted to engage orbiting scroll 154 to define a series of crescent shaped working fluid receiving chambers. These include an unsealed suction chamber SC for the fluid of lower pressure being admitted, a sealed compression receiving chamber of increased pressure being compressed, and a central compression chamber ZC where the compression is completed being exhausted via the discharge port 166 and the discharge valve assembly 192. The fluid suction chamber SC is adapted to communicate with the suction window SW so as to be able to receive the low-pressure working fluid sucked from the suction window SW.
The scroll compressor 100 also includes a lubrication system that is primarily used to provide lubrication to the various relatively moving components of the compressor, such as the compression mechanism CM, main bearings 182, eccentric pins 139, unloader bushings 190, and drive bearings. The lubrication system Bao Shi includes an oil sump OR (main lubricant source) as mentioned above, an oil supply passage provided in the drive shaft 134 including a center hole 135 at a lower portion of the drive shaft and an eccentric hole 136 at an upper portion of the drive shaft, a lubrication eccentric pin 139, a lubricant storage area (sub-lubricant source) for temporarily storing lubricant temporarily staying in the main bearing housing 180 after the lubrication eccentric pin 139, the unloading bushing 190, the drive bearing and/OR the main bearing 182, a compression mechanism oil supply configuration CO (see fig. 2) for supplying lubricant from the lubricant storage area to the compression mechanism CM, and an oil return passage for returning the lubricant from the lubricant storage area to the oil sump OR.
In particular, the lubricant reservoir includes a lubricant reservoir OA (base region of the orbiting scroll end plate) located between the eccentric pin 139, the unloading bushing 190 and/or the top end surface of the drive bearing and the lower surface of the orbiting scroll end plate 152 and located in the hub 156 (see fig. 2).
When the scroll compressor 100 is operated, the electric motor 132 is energized to rotate the rotor 138 integrally with the drive shaft 134. At this time, the eccentric pin 139 integrally formed with the drive shaft 134 also rotates, and the hub 156 is driven via the unloading bushing 190 and/or the drive bearing, whereby the orbiting scroll member 150 is made to perform translational rotation, i.e., orbit, with respect to the fixed scroll member 160 via the cross slip ring 199 (i.e., the axis of the orbiting scroll member 150 revolves with respect to the axis of the fixed scroll member 160, but both the orbiting scroll member 150 and the fixed scroll member 160 do not themselves rotate about their respective axes). At the same time, low pressure working fluid drawn from suction fitting 194 passes through main bearing housing 180 along main bearing housing passage PG and then into compression mechanism CM (specifically into fluid suction chamber SC) via suction window SW.
Thereby, each of the accommodation chambers defined by the fixed scroll 164 and the movable scroll 154 changes from the unsealed fluid suction chamber SC to the compression accommodation chamber to the central compression chamber ZC (having the discharge pressure) in the process of moving from the radially outer side to the radially inner side, and the volume gradually becomes smaller from large. In this way, the pressure in the accommodation chamber also gradually increases, so that the working fluid is compressed and eventually discharged from the discharge port 166 to the discharge pressure region HR and further discharged to the outside of the compressor via a discharge fitting (not shown).
Meanwhile, the lubricant can be transferred from the oil sump OR to a lubricant storage area (such as the lubricant storage area OA) via the oil supply passage (specifically, the center hole 135 and the eccentric hole 136) by centrifugal force generated by the rotation of the driving shaft 134. Then, by the compression mechanism oil supply configuration CO, a part of the lubricant temporarily stored in the lubricant storage area OA is supplied to the compression mechanism CM (e.g., to an appropriate area of the fluid suction chamber SC) so as to provide lubrication to the compression mechanism CM. Then, the remaining lubricant temporarily stored in the lubricant storage area OA is returned to the oil sump OR through the oil return passage.
The case of the compression mechanism oil supply structure CO of the lubrication system of the comparative example will be described below with reference to fig. 2 (fig. 2 is a longitudinal sectional view showing an orbiting scroll member incorporating the compression mechanism oil supply structure of the comparative example).
The compression mechanism oil supply structure CO includes an oil inlet end (oil inlet hole) 201 communicating with the lubricant reservoir area OA, and a lateral hole 205 communicating with the oil inlet end 201. An oil inlet end 201 and a cross bore 205 are formed in the orbiting scroll end plate 152. The oil inlet end 201 is an axial hole extending in the axial direction. An opening position (outflow opening position) of the cross hole 205 at the outer peripheral surface 152a is set to be in the flow path of the sucked low-pressure working fluid. Suction fitting 194 is disposed in alignment with main bearing housing passage PG.
Also, the transverse bore 205 includes a counterbore 205a at a radially outer section, and the counterbore 205a has an inner diameter that is greater than the inner diameter of the remaining section of the transverse bore 205, and the compression mechanism oil supply configuration CO further includes an oil outlet bore 203 in communication with the appropriate region of the fluid suction chamber SC. The bulkhead 207 is adapted to be coupled to the counterbore 205a, with a through bore 207a provided in the bulkhead 207.
Thus, according to the compression mechanism oil supply configuration of the comparative example, when lubricant from the lubricant reservoir OA is discharged from the opening of the lateral hole 205 to the orbiting scroll end plate 152 during operation of the scroll compressor, the discharged lubricant is actively caused to meet the sucked low pressure working fluid so that the low pressure working fluid can bring a part of the lubricant into the compression mechanism CM. In comparison with a solution in which no active injection means for supplying the compression means are provided, the oil circulation rate can be brought within a suitable range at different compressor speeds and/or at different system operating parameters. In addition, by providing the counter bore, it contributes to reducing the speed at which the lubricant is discharged out of the movable scroll end plate and to improving the mist spray of the lubricant, by additionally providing the outlet hole, it allows the lubricant to be directly delivered to the fluid suction chamber SC, i.e., the compression mechanism CM, thereby appropriately improving the oil circulation rate, and by alternatively providing the plug having the through hole, it improves the degree of freedom of adjustment of the oil circulation rate.
However, the above-mentioned oil supply structure CO is limited by its simple structural design and cannot be adjusted in fuel injection amount or oil circulation rate according to the change of the working conditions to meet the requirements of performance energy efficiency or reliability of the compressor under different working conditions. There are different working conditions (for example, under rated load or light load working condition and high load (such as high rotation speed) or high temperature and other severe working conditions), the problem that too little oil injection or too much oil injection causes the energy efficiency or reliability of the compressor.
In view of the above, the present invention proposes an inventive concept in which different operating conditions (described by, for example, suction and discharge pressures, evaporation and condensation pressures, suction and discharge temperatures) correspond to different compressor loads, and thus the pressure difference between the discharge and suction pressures can be used to adjust the injection quantity at different compressor loads (i.e., to construct a dynamic correspondence of operating conditions to injection quantity, for example, to increase injection quantity at high load and high differential pressure, and to decrease injection quantity at rated load or low load and low differential pressure) to improve the energy efficiency or reliability of the compressor system.
The scroll compression mechanism with an oil supply structure of the present invention will be mainly described below with reference to fig. 3 and 4 and fig. 1 and 2, and components substantially other than the oil supply structure are substantially the same or similar as those of the compressor of the comparative example, and reference numerals of the same components in the scroll compressor of the comparative example incorporating the oil supply structure continue to be used.
The oil supply structure of the scroll compression mechanism of the present invention includes an oil supply passage provided in the orbiting scroll end plate 152 for supplying lubricating oil from a lubricating oil source into the scroll compression mechanism CM, a regulating valve 320, and a fluid pressure passage 330. The regulator valve 320 includes a movable valve body 321, and the fluid pressure passage 330 includes a first end 331 and a second end 332, the first end 331 being in fluid communication with a high-pressure side central compression chamber ZC (which is in fluid communication with a discharge pressure region HR) to apply a higher first/discharge pressure to a first/high-pressure side end of the movable valve body 321, the second end 332 being in communication with a suction pressure region/low-pressure region SP located outside the scroll compression mechanism CM to apply a lower second/suction pressure to a second/low-pressure side end of the movable valve body 321, such that the movable valve body 321 is selectively movable in a first direction to reduce the flow cross-sectional area of the oil supply passage and in a second direction opposite to the first direction to increase the flow cross-sectional area of the oil supply passage based on a pressure difference of the first/discharge pressure and the second/suction pressure, thereby regulating the amount of oil supplied to the compression mechanism CM according to a pressure difference corresponding to a change in operating condition.
With the above oil supply configuration, the oil injection amount or the oil circulation rate can be dynamically adjusted according to the change of the operating condition such that, for example, under the high load (high suction and discharge temperatures, high condensing and evaporating temperatures) as the pressure difference between the discharge pressure and the suction pressure becomes larger, the oil injection amount is correspondingly increased such that the increased oil circulation rate ensures a sufficient lubricant lubrication requirement to ensure the stability and reliability of the operation of the compressor system, and the oil injection amount is correspondingly reduced under the rated load or light load to improve the energy efficiency of the compressor system.
In experimental tests, for example, at 45/95, 45/120, 55/150, 40/150 at different evaporating/condensing temperatures, the compression mechanism of the prior art oil supply configuration provided a substantially constant oil circulation rate of 1.5% such that at low evaporating/condensing temperatures too high an oil lubrication rate was provided and at high evaporating/condensing temperatures too low an oil lubrication rate was exceeded by the desired range of oil lubrication rates. In contrast, the compression mechanism of the oil supply configuration according to the present invention provides for adaptively varying oil circulation rates of 0.5%, 1.5% and 1.4% so that the oil circulation rate at each operating condition can be within a desired range of oil lubrication rates at the respective operating conditions.
It will be appreciated by those skilled in the art that while the lower pressure source is illustrated as a low pressure region SP located outside the scroll compression mechanism CM, the lower pressure source may also be an unsealed intake lower pressure fluid intake chamber SC.
In fig. 3 and 4, similarly to the comparative example, an oil outlet hole 203 communicating with an appropriate region of the fluid suction chamber SC is provided on the orbiting scroll end plate 152, and the oil outlet hole 203 may be in the form of a vertical hole or an inclined hole and be a part of an oil supply duct. In an embodiment of the present application, the oil outlet opening 203 is a vertical oil supply duct that is substantially parallel to the central axis of the scroll compression mechanism. The movable valve body 321 is partially disposed in the vertical oil supply duct 203 so as to adjust the flow cross-sectional area of the oil supply passage by adjusting the flow cross-sectional area of the vertical oil supply duct 203. The oil supply passages 310, 310' also include a lateral oil supply duct substantially perpendicular to the central axis of the scroll compression mechanism CM, which is in intersecting communication with the vertical oil supply duct 203 to supply lubricating oil from a lubricating oil source into the scroll compression mechanism CM.
As shown in fig. 3 and 4, the fluid pressure passage 330 may include a transverse fluid pressure port 333 that is generally perpendicular to the central axis of the scroll compression mechanism CM. The lateral fluid pressure port 333 may be disposed horizontally or vertically with the lateral oil supply port in the orbiting scroll end plate 152 according to actual needs such as the shape and configuration of the orbiting scroll end plate 152, for example, in the case where the orbiting scroll end plate is thick, the lateral fluid pressure port 333 and the lateral oil supply port 311 of the oil supply passage 310 may be disposed vertically as shown in fig. 3.
In an advantageous aspect of the embodiment, the lateral fluid pressure channel 333 and the vertical oil supply channel 203 partly overlap in a vertical direction parallel to the central axis, such that an efficient oil supply channel design is achieved to avoid machining of additional communication channels. In fig. 4, the transverse fluid pressure channel 333 is arranged horizontally with the transverse oil supply channel of the oil supply channel 310', which comprises a main transverse oil supply channel 311' arranged side by side with the transverse fluid pressure channel 333 (via the oil inlet end 201) in communication with the lubricant source. And, the lateral oil supply port further includes a secondary lateral oil supply port 312 'in intersecting communication with both the primary lateral oil supply port 311' and the vertical oil supply port 203, i.e., the primary lateral oil supply port 311 'is in intersecting communication with the vertical oil supply port 203 through the secondary lateral oil supply port 312'. It will be appreciated that the transverse oil supply port may include only a main transverse oil supply port 311', and that the main transverse oil supply port 311' may be in direct intersecting communication with the vertical oil supply port 203 as opposed to the oblique oil supply port of the transverse fluid pressure port 333. In fig. 3, the lateral fluid pressure gallery 333 is arranged vertically and side-by-side with the lateral oil supply gallery 311, wherein the lateral oil supply gallery 311 communicates with the lubricant source (via the oil inlet end 201) and is in intersecting communication with the vertical oil supply gallery 203. In fact, this arrangement results in the lateral oil supply channel 311, the vertical oil supply channel 203 and the lateral fluid pressure channel 333 being substantially in the same vertical plane, so that a more efficient oil supply channel design is achieved.
The regulator valve 320 further includes an elastic member 322 provided so as to be able to abut against the second/low pressure side end of the movable valve body 321. The resilient member 322 is shown as a spring having one end connected to a plug disposed in a counterbore at a radially outer section of the lateral fluid pressure port 333 and the other end connected to a second/low pressure side end of the movable valve body 321 adapted to bias the movable valve body 321 toward the first/high pressure side direction.
The movable valve body 321 includes a connection section connecting the first/high pressure side end and the second/low pressure side end, the connection section being tapered with respect to the first/high pressure side end and the second/low pressure side end, the connection section being shown as a stepped surface, and may be a curved surface or a tapered surface. The tapered connecting section has a diameter smaller than the diameter of the first/high pressure side end and smaller than the diameter of the second/low pressure side end. At different conditions of the compressor, for example, at rated load or light load, the differential pressure of the first/discharge pressure and the second/suction pressure is smaller than the biasing force of the elastic member, so that the movable valve body 321 moves toward the first/high pressure side, the tapered connecting section occupies less (more at the lower pressure side end of the larger diameter) in the oil supply passage such as the vertical oil supply passage 203 to reduce the flow cross-sectional area of the oil supply passage, thereby reducing the amount of oil injection, and at high load, the differential pressure of the first/discharge pressure and the second/suction pressure is larger than the biasing force of the elastic member, so that the movable valve body 321 moves toward the second/low pressure side, and the tapered connecting section occupies more (less at the lower pressure side end of the larger diameter) in the vertical oil supply passage 203 to increase the flow cross-sectional area of the oil supply passage, thereby increasing the amount of oil injection.
The base area OA of the interior space of the hub 156 of the orbiting scroll member 150 adjacent the orbiting scroll end plate 152 is shown as a source of lubrication oil with the oil feed end 201 of the oil supply passage connected to the base area OA. The sump OR stored at the bottom of the interior volume IV within the housing 110 may also be used as a source of lubricating oil.
It will be appreciated by those skilled in the art that the first pressure varies with the operating conditions of the scroll compression mechanism CM or with the operating conditions of the system to which the scroll compression mechanism CM is applied, and/or the second pressure varies with the operating conditions of the scroll compression mechanism CM or with the operating conditions of the system to which the scroll compression mechanism CM is applied.
In this document, the use of the azimuthal terms "lateral," "vertical," and the like are for descriptive purposes only and should not be construed as limiting.
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 specific embodiments described and illustrated herein, and that various changes in the exemplary embodiments may be made by those skilled in the art without departing from the scope defined by the claims.
Claims (12)
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010579961.8A CN113833659B (en) | 2020-06-23 | 2020-06-23 | Scroll compression mechanism and scroll compressor |
| US18/012,247 US20230258186A1 (en) | 2020-06-23 | 2020-10-23 | Scroll compression mechanism and scroll compressor |
| PCT/CN2020/123044 WO2021258585A1 (en) | 2020-06-23 | 2020-10-23 | Scroll compression mechanism and scroll compressor |
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| CN202010579961.8A CN113833659B (en) | 2020-06-23 | 2020-06-23 | Scroll compression mechanism and scroll compressor |
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| CN113833659A CN113833659A (en) | 2021-12-24 |
| CN113833659B true CN113833659B (en) | 2025-02-14 |
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|---|---|---|---|---|
| JPS62178791A (en) * | 1986-02-03 | 1987-08-05 | Matsushita Electric Ind Co Ltd | Scroll compressor |
| CN106194750A (en) * | 2015-04-30 | 2016-12-07 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
| CN212643056U (en) * | 2020-06-23 | 2021-03-02 | 艾默生环境优化技术(苏州)有限公司 | Scroll Compression Mechanisms and Scroll Compressors |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002180981A (en) * | 2000-12-12 | 2002-06-26 | Toyota Industries Corp | Scroll type compressor |
| US7815423B2 (en) * | 2005-07-29 | 2010-10-19 | Emerson Climate Technologies, Inc. | Compressor with fluid injection system |
| US7566210B2 (en) * | 2005-10-20 | 2009-07-28 | Emerson Climate Technologies, Inc. | Horizontal scroll compressor |
| US10641269B2 (en) * | 2015-04-30 | 2020-05-05 | Emerson Climate Technologies (Suzhou) Co., Ltd. | Lubrication of scroll compressor |
| KR101974854B1 (en) * | 2015-10-29 | 2019-05-03 | 에머슨 클리메이트 테크놀로지즈 인코퍼레이티드 | A compressor including a capacity modulation system |
| CN105464989B (en) * | 2015-12-24 | 2018-03-23 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of fueller, there is its screw compressor and control method |
| CN205744457U (en) * | 2016-05-18 | 2016-11-30 | 艾默生环境优化技术(苏州)有限公司 | Oil supply device for compressor and compressor |
| JP7000136B2 (en) * | 2017-11-29 | 2022-01-19 | 三菱重工サーマルシステムズ株式会社 | Scroll compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62178791A (en) * | 1986-02-03 | 1987-08-05 | Matsushita Electric Ind Co Ltd | Scroll compressor |
| CN106194750A (en) * | 2015-04-30 | 2016-12-07 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
| CN212643056U (en) * | 2020-06-23 | 2021-03-02 | 艾默生环境优化技术(苏州)有限公司 | Scroll Compression Mechanisms and Scroll Compressors |
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Address after: No. 69 Suhong West Road, Industrial Park, Suzhou City, Jiangsu Province, 215101 Applicant after: Gulun Environmental Technology (Suzhou) Co.,Ltd. Address before: Emerson R & D and overall solution center, No. 35, Suhong West Road, Suzhou Industrial Park, Suzhou, Jiangsu, 215021 Applicant before: EMERSON CLIMATE TECHNOLOGIES (SUZHOU) Co.,Ltd. |
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