CN110925194A - Thrust plate, movable scroll member and scroll compressor - Google Patents
Thrust plate, movable scroll member and scroll compressor Download PDFInfo
- Publication number
- CN110925194A CN110925194A CN201811117545.5A CN201811117545A CN110925194A CN 110925194 A CN110925194 A CN 110925194A CN 201811117545 A CN201811117545 A CN 201811117545A CN 110925194 A CN110925194 A CN 110925194A
- Authority
- CN
- China
- Prior art keywords
- groove
- orbiting scroll
- scroll member
- thrust plate
- thrust
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000005461 lubrication Methods 0.000 claims abstract description 30
- 230000007704 transition Effects 0.000 claims description 10
- 239000003507 refrigerant Substances 0.000 abstract description 10
- 239000003921 oil Substances 0.000 description 47
- 239000010687 lubricating oil Substances 0.000 description 46
- 239000000314 lubricant Substances 0.000 description 28
- 230000000694 effects Effects 0.000 description 12
- 239000000428 dust Substances 0.000 description 8
- 239000012530 fluid Substances 0.000 description 6
- 230000006835 compression Effects 0.000 description 5
- 238000007906 compression Methods 0.000 description 5
- 230000002542 deteriorative effect Effects 0.000 description 4
- 230000017525 heat dissipation Effects 0.000 description 4
- 238000003754 machining Methods 0.000 description 4
- 238000006748 scratching Methods 0.000 description 4
- 230000002393 scratching effect Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 3
- 239000003595 mist Substances 0.000 description 3
- 238000005192 partition Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 2
- 238000005266 casting Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000003860 storage Methods 0.000 description 2
- 229910002092 carbon dioxide Inorganic materials 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Images
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
-
- 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
-
- 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
Abstract
The invention provides a thrust plate (40) for a scroll compressor, an orbiting scroll member (60) and a scroll compressor. The thrust plate (40) includes a thrust surface (S1) for supporting an orbiting scroll member (60), wherein the thrust surface (S1) is formed with a groove (W) in a curved shape extending radially from a radially inner side to a radially outer side of the thrust plate (40). The orbiting scroll member (60) includes a thrust surface (S2) for being supported by a thrust plate (40), wherein the thrust surface (S2) is formed with a groove (W) having a curved shape, the groove (W) extending radially centering on an axis of the orbiting scroll member (60). This arrangement makes it possible to provide good lubrication between the thrust plate (40) and the orbiting scroll member (60) in each case, particularly when different refrigerants are used.
Description
Technical Field
The invention relates to a thrust plate for a scroll compressor, an orbiting scroll member for a scroll compressor and a scroll compressor.
Background
The statements in this section merely provide background information related to the present disclosure and may not constitute prior art.
A scroll compressor generally includes a compression mechanism composed of a fixed scroll member and a movable scroll member. The orbiting scroll member is supported by a thrust plate to provide axial restraint. In prior art scroll compressors, both the thrust surface of the orbiting scroll member and the thrust surface of the thrust plate are formed as substantially flat surfaces. The refrigerant of a commonly used scroll compressor includes carbon dioxide, R410, etc. When a special refrigerant such as R32 is used, the temperature of the thrust surface can reach 150 degrees fahrenheit, much higher than when a conventional refrigerant is used, resulting in poor lubrication between the orbiting scroll member and the thrust surface of the thrust plate and severe wear on the orbiting scroll member and the thrust surface of the thrust plate.
Accordingly, it is desirable to provide a thrust surface configuration that provides good lubrication between the orbiting scroll member and the thrust plate under various conditions, particularly when different refrigerants are used.
Disclosure of Invention
It is an object of the present invention to provide a thrust surface configuration that provides good lubrication between an orbiting scroll member and a thrust plate under various conditions, particularly when different refrigerants are used.
According to an aspect of an embodiment of the present invention, there is provided a thrust plate for a scroll compressor, including a thrust surface for supporting an orbiting scroll member, wherein the thrust surface is formed with a groove in a curved shape extending radially from a radially inner side of the thrust plate to a radially outer side thereof, so that lubrication between the thrust plate and the orbiting scroll member can be improved. The curved grooves have a longer groove length than the straight grooves to enable a smaller number of grooves to cover more area of the thrust surface, thereby providing a more uniform and effective lubrication effect. And the radial groove is arranged, so that partial lubricating oil can be stored through the groove, and the lubricating oil is convenient to be brought from the inner side of the thrust plate to the outer side of the thrust plate and from the groove to the position between the movable scroll part and the thrust plate when the movable scroll part translates, so that the abrasion of the movable scroll part and the thrust plate is avoided by increasing the supply of the lubricating oil. In addition, the lubricating oil stored in the groove also has a certain heat dissipation effect so as to avoid the lubricating oil from deteriorating due to overhigh oil temperature. The grinding dust generated during the movement of the movable vortex can be brought into the grooves and then discharged through the oil flow, so that the grinding dust is prevented from continuously damaging the bearing surface in the thrust bearing.
According to another aspect of the embodiment of the present invention, in the thrust plate, the groove (W) is a plurality of grooves (W) which are symmetrically arranged.
According to another aspect of the embodiments of the present invention, in the thrust plate, the curve is an arc, a spiral, or an involute.
According to another aspect of the embodiment of the invention, in the thrust plate, the groove and a central circle of the movable scroll part do not have a common tangent, wherein a motion track of an axis of the movable scroll part forms the central circle of the movable scroll part, so that the phenomenon that an edge of the groove cuts the movable scroll part and lubricating oil in the groove cannot be brought to a thrust surface when the movable scroll part translates is avoided.
According to another aspect of the embodiment of the present invention, in the thrust plate, oil reservoirs having a width larger than that of the intermediate oil passage of the groove are provided at both ends of the groove. By setting larger width at two ends of the groove, lubricating oil can be stored in the oil storage part at the inner side, and the lubricating oil is brought into the middle oil way of the groove through the movement of the movable scroll part. When the lubricant finally reaches the wide outer oil reservoir, the outer oil reservoir may store a part of the lubricant to prevent the lubricant from flowing out of the thrust plate by inertia, and may also bring the lubricant in the outer oil reservoir back to the thrust surface by the movement of the orbiting scroll member to continue lubrication.
According to another aspect of the embodiment of the present invention, in the thrust plate, the depth of the groove is equal to or less than the width of the groove, so that it is possible to avoid a decrease in the lubricating effect due to an excessively deep groove.
According to another aspect of the embodiment of the present invention, in the thrust plate, the width of the groove is 1mm or more, so that oil droplets of lubricating oil, for example, a minimum of 10 oil droplets having a diameter of 0.2mm, can smoothly pass through the groove.
According to another aspect of the embodiment of the present invention, in the thrust plate, a cross-sectional shape of the groove is a semicircle, a V, or a square.
According to another aspect of an embodiment of the present invention, in the thrust plate, the groove smoothly transitions to a surface of the thrust surface where the groove is not located, thereby facilitating bringing lubricant in the groove to the thrust surface and not scratching the orbiting scroll member.
According to another aspect of an embodiment of the present invention, there is provided an orbiting scroll member for a scroll compressor including a thrust surface for being supported by a thrust plate, wherein the thrust surface is formed with a groove having a curved shape, the groove radially extending centering on an axis of the orbiting scroll member, thereby enabling improved lubrication between the thrust plate and the orbiting scroll member. The curved grooves have a longer groove length than the straight grooves to enable a smaller number of grooves to cover more area of the thrust surface, thereby providing a more uniform and effective lubrication effect. And the radial groove is arranged, so that partial lubricating oil can be stored through the groove, and the lubricating oil is convenient to be brought from the inner side of the thrust plate to the outer side of the thrust plate and from the groove to the position between the movable scroll part and the thrust plate when the movable scroll part translates, so that the abrasion of the movable scroll part and the thrust plate is avoided by increasing the supply of the lubricating oil. In addition, the lubricating oil stored in the groove also has a certain heat dissipation effect so as to avoid the lubricating oil from deteriorating due to overhigh oil temperature. The grinding dust generated during the movement of the movable vortex can be brought into the grooves and then discharged through the oil flow, so that the grinding dust is prevented from continuously damaging the bearing surface in the thrust bearing.
According to another aspect of the embodiment of the present invention, in the orbiting scroll part, the groove (W) is a plurality of grooves (W) which are symmetrically disposed.
According to another aspect of an embodiment of the present invention, in the orbiting scroll part, the curve is an arc, a spiral or an involute.
According to another aspect of an embodiment of the present invention, in the orbiting scroll part, the groove has no common tangent with a central circle of the orbiting scroll part, wherein a movement locus of an axis of the orbiting scroll part forms the central circle of the orbiting scroll part, thereby preventing an edge of the groove from cutting a thrust plate and preventing lubricant in the groove from being brought to a thrust surface when the orbiting scroll part is in translation.
According to another aspect of an embodiment of the present invention, in the orbiting scroll part, oil reservoirs having a width larger than that of the middle oil passage of the groove are provided at both ends of the groove. By setting larger width at two ends of the groove, lubricating oil can be stored in the oil storage part at the inner side, and the lubricating oil is brought into the middle oil way of the groove through the movement of the movable scroll part. When the lubricant finally reaches the wide outer oil reservoir, the outer oil reservoir may store a part of the lubricant to prevent the lubricant from flowing out of the thrust plate by inertia, and may also bring the lubricant in the outer oil reservoir back to the thrust surface by the movement of the orbiting scroll member to continue lubrication.
According to another aspect of the embodiment of the present invention, in the orbiting scroll part, the depth of the groove is equal to or less than the width of the groove, so that it is possible to prevent the lubrication effect from being weakened due to the depth of the groove being too deep.
According to another aspect of the embodiment of the present invention, in the orbiting scroll part, the width of the groove is 1mm or more, thereby facilitating smooth passage of oil droplets of lubricating oil, for example, a minimum of 10 oil droplets having a diameter of 0.2mm, through the groove.
According to another aspect of the embodiment of the present invention, in the orbiting scroll part, the cross-sectional shape of the groove is a semicircle, a V shape, or a square shape.
According to another aspect of an embodiment of the present invention, in the orbiting scroll member, the groove smoothly transitions to a surface of the thrust surface where the groove is not provided, thereby facilitating bringing the lubricant in the groove to the thrust surface and not scratching the thrust plate.
According to another aspect of an embodiment of the present invention, in the orbiting scroll part, the orbiting scroll part further includes a boss and a transition portion disposed between the thrust surface and the boss, wherein the groove extends longest from a radially outer side of the thrust surface toward the boss to a boundary of the thrust surface and the transition portion, thereby avoiding an influence on the boss of the orbiting scroll part.
According to another aspect of the embodiment of the present invention, in the orbiting scroll part, wherein a distance in the radial direction between both ends of the groove is equal to or greater than a distance in the radial direction between a radially inner side and a radially outer side of the thrust plate, thereby facilitating bringing the lubricating oil in the groove to the entire thrust surface of the thrust plate for sufficient lubrication.
According to another aspect of an embodiment of the present invention there is provided a scroll compressor comprising at least one of the thrust plate according to the above and at least one of the orbiting scroll member according to the above.
Drawings
The features and advantages of one or more embodiments of the present invention will become more readily understood from the following description taken in conjunction with the accompanying drawings, in which:
FIG. 1 is a longitudinal sectional view of a conventional scroll compressor;
FIG. 2 is a perspective view of a thrust plate in the scroll compressor shown in FIG. 1;
FIG. 3 is a perspective view of the orbiting scroll member of the scroll compressor shown in FIG. 1;
fig. 4 is a perspective view of a thrust plate according to a first embodiment of the present invention;
fig. 5 is a perspective view of a thrust plate according to a second embodiment of the present invention;
fig. 6 is a perspective view of a thrust plate according to a third embodiment of the present invention;
fig. 7 is a perspective view of a thrust plate according to a fourth embodiment of the present invention;
FIG. 8 is a schematic illustration of the movement of an orbiting scroll member with respect to a thrust plate in accordance with an embodiment of the present invention, with the orbiting scroll member shown in transparency;
FIG. 9 is a perspective view of an orbiting scroll member according to a fifth embodiment of the present invention;
FIG. 10 is a perspective view of an orbiting scroll member in accordance with a sixth embodiment of the present invention;
FIG. 11 is a perspective view of an orbiting scroll member in accordance with a seventh embodiment of the present invention;
FIG. 12 is a perspective view of an orbiting scroll member in accordance with an eighth embodiment of the present invention;
fig. 13-15 are cross-sectional views of grooves according to embodiments of the present invention.
Detailed Description
The following description of various embodiments of the invention is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses. The same reference numerals are used to designate the same components in the respective drawings, and thus the configurations of the same components will not be described repeatedly. The dimensional relationships of the various configurations in the drawings are merely exemplary and do not represent actual dimensional relationships.
The general construction and operating principle of the scroll compressor will first be described with reference to fig. 1. As shown in fig. 1, a scroll compressor 100 (hereinafter sometimes referred to as a compressor) generally includes a housing 110, a top cover 112 disposed at one end of the housing 110, a bottom cover 114 disposed at the other end of the housing 110, and a partition 116 disposed between the top cover 112 and the housing 110 to partition an internal space of the compressor into a high pressure side and a low pressure side. The space between the diaphragm 116 and the top cover 112 constitutes a high pressure side, on which a discharge connection 119 for discharging compressed fluid is provided. And the space between the partition 116, the housing 110, and the bottom cover 114 constitutes a low pressure side. A motor 120 including a stator 122 and a rotor 124 is provided in the housing 110. A drive shaft 130 is provided in the rotor 124 to drive a compression mechanism constituted by a fixed scroll member 150 and an orbiting scroll member 160. Orbiting scroll member 160 includes an end plate 164, a hub 162 formed on one side of the end plate, and a spiral vane 166 formed on the other side of the end plate. The non-orbiting scroll member 150 includes an end plate 154, a spiral vane 156 formed at one side of the end plate, and an exhaust port 152 formed at a substantially central position of the end plate. A series of compression chambers, the volume of which gradually decreases from the radially outer side to the radially inner side, are formed between the spiral vane 156 of the non-orbiting scroll 150 and the spiral vane 166 of the orbiting scroll 160.
One side of orbiting scroll member 160 is supported by an upper portion (i.e., a support portion) of thrust plate 140. One end of drive shaft 130 is provided with an eccentric crank pin 132 and a relief bushing 142 is provided between eccentric crank pin 132 and a hub 162 of orbiting scroll member 160. Orbiting scroll member 160 will be rotated in translation relative to non-orbiting scroll member 150 (i.e., the axis of orbiting scroll member 160 rotates about the axis of non-orbiting scroll member 150, but orbiting scroll member 160 does not itself rotate about its axis) by the actuation of motor 120 to effect compression of the fluid. The fluid compressed by the non-orbiting scroll part 150 and the orbiting scroll part 160 is discharged to a high pressure side through the discharge port 152. To prevent fluid on the high pressure side from flowing back to the low pressure side via the exhaust port 152 under certain conditions, a one-way valve or exhaust valve 170 may be provided at the exhaust port 152.
The lubrication process of each component in the compressor will be described below. In the example of the scroll compressor shown in fig. 1, lubricating oil is stored in the bottom of the compressor housing. Accordingly, a passage extending substantially in the axial direction thereof, i.e., a center hole 136 formed at the lower end of the drive shaft 130 and an eccentric hole 134 extending upward from the center hole 136 to the end surface of the eccentric crank pin 132, is formed in the drive shaft 130. The end of the central bore 136 is submerged in or otherwise supplied with lubricant at the bottom of the compressor housing. In one example, a lubrication supply, such as an oil pump or oil fork, may be disposed in or near the central bore 136. During operation of the compressor, one end of the central bore 136 is supplied with lubricating oil by the lubricating oil supply, and the lubricating oil entering the central bore 136 is pumped or thrown into the eccentric bore 134 by centrifugal force during rotation of the drive shaft 130 and flows up the eccentric bore 134 to the end face of the eccentric crank pin 132. The lubricant discharged from the end face of eccentric crank pin 132 flows down through thrust plate 140 along the gap between unload bushing 142 and eccentric crank pin 132 and the gap between unload bushing 142 and hub 162, and a portion of the lubricant is agitated by hub 162 to move up to the underside of end plate 164 of orbiting scroll member 160 and spread over the thrust surface between orbiting scroll member 160 and thrust plate 140 as orbiting scroll member 160 rotates in translation. During operation of the compressor, the lubricating oil supplied to various moving parts in the compressor is thrown and splashed to form droplets or mist. These lubricant droplets or mist will be mixed in the working fluid (or refrigerant). The working fluid mixed with lubricant droplets is then drawn into the compression chambers between non-orbiting scroll member 150 and orbiting scroll member 160 to effect lubrication, sealing and cooling of the interior of these scroll members. This lubrication between the orbiting and non-orbiting scroll members is commonly referred to as oil mist lubrication.
As shown in FIGS. 2 and 3, thrust surface T1 of thrust plate 140 and thrust surface T2 of orbiting scroll member 160 are generally formed as flat planar surfaces. During the translational rotation of the orbiting scroll member, the lubricating oil between the thrust surfaces T1 and T2 rises in pressure within a range to generate hydrodynamic pressure that separates the two thrust surfaces T1 and T2 from each other, thereby forming a lubricating oil film capable of providing good lubrication (i.e., forming a so-called wedge effect). In addition, the lubricating oil between the thrust surfaces T1 and T2 is reduced in pressure in another range so that the lubricating oil film is broken. Through the process, the movable scroll part floats on the thrust plate through the lubricating oil hydrodynamic pressure lubricating oil film in the translation and rotation process, so that the friction force between the movable scroll part and the thrust plate is effectively reduced.
However, in some particular cases, good lubrication may not be provided between the orbiting scroll member and the thrust plate. For example, in the case of R32 being used as the refrigerant, the temperature of the thrust surface can reach 150 degrees fahrenheit, much higher than that of the thrust surface when a conventional refrigerant is used, resulting in poor lubrication between the thrust surfaces of the orbiting scroll member and the thrust plate and severe wear on the thrust surfaces of the orbiting scroll member and the thrust plate.
According to the embodiment of the invention, even in the case of using a new refrigerant, good lubrication can be formed between the thrust surface of the orbiting scroll member and the thrust surface of the thrust plate.
The configuration of the thrust plate 40 according to the first to fourth embodiments of the present invention will be described below with reference to fig. 4 to 7.
As shown in fig. 4, in the scroll compressor of the first embodiment of the present invention, there is provided a thrust plate 40 including a thrust surface S1 for supporting the orbiting scroll member 60, wherein the thrust surface S1 is provided with a groove W in a straight line shape extending radially from a radially inner side to a radially outer side of the thrust surface S1. By the arrangement of the groove W, it is possible to store part of the lubricating oil through the groove W, and to facilitate bringing the lubricating oil from the inner side of the thrust plate 40 to the outer side of the thrust plate 40 and bringing the lubricating oil from the groove W to between the orbiting scroll member and the thrust plate upon the orbiting scroll member translating, thereby avoiding the orbiting scroll member and the thrust plate from being worn by increasing the supply of the lubricating oil. Moreover, the lubricating oil stored in the groove W also has a certain heat dissipation function so as to avoid the lubricating oil from deteriorating due to overhigh oil temperature. And the abrasive dust generated during the movement of the movable vortex can be brought into the groove W and then discharged through the oil flow, so that the condition that the bearing surface is continuously damaged by the abrasive dust in the thrust bearing is avoided. The grooves W are a plurality of grooves, and the grooves W can be symmetrically or asymmetrically arranged. Preferably, in order to facilitate smooth passage of oil droplets of lubricating oil, for example, a minimum of 10 oil droplets having a diameter of 0.2mm, through the grooves W, the width of the grooves W may be set to 1mm or more. Preferably, the depth of the groove W is equal to or less than the width of the groove W in order to avoid a reduction in the lubrication effect caused by an excessively deep depth of the groove W. Preferably, to facilitate bringing the lubricant in the groove W to the thrust surface S1 and not scratching the orbiting scroll member 60, the groove W may be smoothly transitioned to the surface of the thrust surface S1 not provided with the groove W, for example, by rounding, chamfering, or the like. Preferably, the groove W may be manufactured by machining, laser machining, or casting.
In the second to fourth embodiments shown in fig. 5 to 7, the shape of the groove W may be curved. The curvilinear grooves W have a longer groove length than the linear grooves W to enable a smaller number of grooves to cover a greater area of the thrust surface S1, thereby providing a more uniform and effective lubrication effect. Preferably, the curve is an arc, a helix or an involute. Preferably, as shown in fig. 8, the groove W does not have a common tangent with a center circle C of the orbiting scroll member 60, wherein a movement locus of an axis of the orbiting scroll member 60 forms the center circle C of the orbiting scroll member 60. This is because, during translation of orbiting scroll member 60, as orbiting scroll member 60 is subjected to a tilting torque, the contact force between orbiting scroll member 60 and the thrust plate in one region D is large, if the direction of movement of the region D of the orbiting scroll member 60 where the contact force is large is parallel to the direction of any one portion of the groove W, it is liable that the edge of the groove W cuts the orbiting scroll member 60, and the lubricant in the groove W cannot be brought to the thrust surface S1, it is thus required that the moving direction of the region D of the orbiting scroll member 60 where the contact force is large has an angle with the direction of any one portion of the groove W, and, because orbiting scroll member 60 translates, all portions thereof move in the same direction, that is, it is only necessary to have an angle between the direction of movement of the axis of orbiting scroll member 60 and the direction of any one portion of groove W. This condition can be obtained by making the groove W have no common tangent with the center circle C of the orbiting scroll member 60. Preferably, as shown in the second embodiment of fig. 5, the grooves W may take the form of a group of several grooves, each group of grooves being equally spaced apart. Preferably, as shown in the third embodiment of fig. 6, the grooves W may be distributed in such a manner that the intervals between each groove are equal.
Preferably, as shown in the fourth embodiment of fig. 7, oil reservoirs O having a width greater than that of the middle oil passage of the groove W may be provided at both ends of the groove W. By providing the large width at both ends of the groove W, the lubricating oil can be stored in the oil reservoir O on the inner side first, and brought into the intermediate oil passage of the groove W by the movement of the orbiting scroll member. When the lubricant finally reaches the wide outer oil reservoir O, the outer oil reservoir O can store a part of the lubricant to prevent the lubricant from flowing out of the thrust plate by inertia, and can also bring the lubricant in the outer oil reservoir O back to the thrust surface by the movement of the orbiting scroll member to continue lubrication.
The recess W may also be provided on the thrust surface S2 of the orbiting scroll member 60, and the construction of the orbiting scroll member 60 according to the fifth to eighth embodiments of the present invention will be described with reference to fig. 9 to 12.
As shown in fig. 9, in the scroll compressor according to the fifth embodiment of the present invention, an orbiting scroll member 60 including a thrust surface S2 supported by a thrust plate is provided, wherein a groove W extending radially with an axis of the orbiting scroll member 60 as a center and having a straight shape is provided on the thrust surface S2. By the provision of this groove W, it is made possible to store part of the lubricating oil through the groove W and to facilitate bringing the lubricating oil from the inside of the orbiting scroll member 60 to the outside of the orbiting scroll member 60 and bringing the lubricating oil from the groove W to between the orbiting scroll member and the thrust plate upon the orbiting scroll member translating, thereby avoiding the orbiting scroll member and the thrust plate from being worn out by increasing the supply of the lubricating oil. Moreover, the lubricating oil stored in the groove W also has a certain heat dissipation function so as to avoid the lubricating oil from deteriorating due to overhigh oil temperature. And the abrasive dust generated during the movement of the movable vortex can be brought into the groove W and then discharged through the oil flow, so that the condition that the bearing surface is continuously damaged by the abrasive dust in the thrust bearing is avoided. The grooves W are a plurality of grooves, and the grooves W can be symmetrically or asymmetrically arranged. Preferably, in order to facilitate smooth passage of oil droplets of lubricating oil, for example, a minimum of 10 oil droplets having a diameter of 0.2mm, through the grooves W, the width of the grooves W may be set to 1mm or more. Preferably, the depth of the groove W is equal to or less than the width of the groove W in order to avoid a reduction in the lubrication effect caused by an excessively deep depth of the groove W. Preferably, in order to facilitate bringing the lubricant in the groove W to the thrust surface S2 without scratching the thrust plate 40, the groove W may be smoothly transitioned to the surface of the thrust surface S2, which is not provided with the groove W, in a manner such as rounding, chamfering, or the like. Preferably, the groove W may be manufactured by machining, laser machining, or casting.
As shown in fig. 10-12, orbiting scroll member 60 further includes a hub 61 and a transition 62 disposed between thrust surface S2 and hub 61, a groove W extends from radially outward of thrust surface S2 toward hub 62, and the groove W extends longest to the intersection of thrust surface S2 and transition 61, thereby avoiding the groove W from affecting hub 61 of orbiting scroll member 60. Preferably, the distance in the radial direction between both ends of the groove W is equal to or greater than the distance in the radial direction between the radially inner side and the radially outer side of the thrust plate 40, so as to facilitate bringing the lubricating oil in the groove W to the entire thrust surface S1 of the thrust plate 40 for sufficient lubrication. As can also be seen in fig. 10-12, the shape of the groove W may be curved. The curvilinear grooves W have a longer groove length than the linear grooves W to enable fewer grooves to cover more of the area of the thrust surface S2, thereby providing a more uniform and effective lubrication effect. Preferably, the curve is an arc, a helix or an involute. Preferably, the groove W does not have a common tangent with a center circle C of the orbiting scroll member 60, wherein a moving locus of an axis of the orbiting scroll member 60 forms the center circle C of the orbiting scroll member 60. This is because, during translation of orbiting scroll member 60, as orbiting scroll member 60 is subjected to a tilting torque, the contact force between orbiting scroll member 60 and thrust plate 40 in one region D is large, if the direction of movement of the region D of the orbiting scroll member 60 where the contact force is large is parallel to the direction of any one portion of the groove W, it is liable that the edge of the groove W cuts the orbiting scroll member 60, and the lubricant in the groove W cannot be brought to the thrust surface S2, it is thus required that the moving direction of the region D of the orbiting scroll member 60 where the contact force is large has an angle with the direction of any one portion of the groove W, and, because orbiting scroll member 60 translates, all portions thereof move in the same direction, that is, it is only necessary to have an angle between the direction of movement of the axis of orbiting scroll member 60 and the direction of any one portion of groove W. This condition can be obtained by making the groove W have no common tangent with the center circle C of the orbiting scroll member 60. Preferably, as shown in the sixth embodiment of fig. 10, the grooves W may take the form of a group of several grooves, each group of grooves being equally spaced apart. Preferably, as shown in the seventh embodiment of fig. 11, the grooves W may be distributed in such a manner that the intervals between each groove are equal.
Preferably, as shown in the eighth embodiment of fig. 12, oil reservoirs O having a width greater than that of the middle oil passage of the groove W may be provided at both ends of the groove W. By providing the large width at both ends of the groove W, the lubricating oil can be stored in the oil reservoir O on the inner side first, and brought into the intermediate oil passage of the groove W by the movement of the orbiting scroll member. When the lubricant finally reaches the wide outer oil reservoir O, the outer oil reservoir O can store a part of the lubricant to prevent the lubricant from inertially flowing out of the movable scroll member 60, and can also bring the lubricant in the outer oil reservoir O back to the thrust surface by the movement of the movable scroll member to continue lubrication.
As shown in fig. 12-13, the groove W may take a semicircular, square, V-shaped cross-sectional shape. Other cross-sectional shapes for the groove W are also possible.
Grooves may be provided in either thrust plate 40 or orbiting scroll member 60 or both thrust plate 40 and orbiting scroll member 60.
While various embodiments and modifications of the present invention have been specifically described above, it will be understood by those skilled in the art that the present invention is not limited to the specific embodiments and modifications described above but may include other various possible combinations and combinations.
Claims (21)
1. A thrust plate (40) for a scroll compressor comprising a thrust surface (S1) for supporting an orbiting scroll member (60), wherein the thrust surface (S1) is formed with a groove (W) in the shape of a curve extending from a radially inner side of the thrust plate (40) to a radially outer side thereof, whereby lubrication between the thrust plate (40) and the orbiting scroll member (60) can be improved.
2. The thrust plate (40) of claim 1, wherein said groove (W) is plural, and said plural grooves (W) are symmetrically arranged.
3. The thrust plate (40) of claim 1 or 2, wherein the curve is an arc, a helix or an involute.
4. The thrust plate (40) of claim 1 or 2, wherein said recess (W) has no common tangent with a center circle (C) of said orbiting scroll member (60), wherein a locus of motion of an axis of said orbiting scroll member (60) forms said center circle (C) of said orbiting scroll member (60).
5. The thrust plate (40) according to claim 1 or 2, wherein at least one of both ends of the groove (W) is provided with an oil reservoir (O) having a width larger than a width of a middle oil passage of the groove (W).
6. The thrust plate (40) of claim 1 or 2, wherein a depth of the groove (W) is less than or equal to a width of the groove (W).
7. The thrust plate (40) of claim 1 or 2, wherein the width of the groove (W) is equal to or greater than 1 mm.
8. The thrust plate (40) of claim 1 or 2, wherein the cross-sectional shape of the groove (W) is semi-circular, V-shaped, or square.
9. The thrust plate (40) of claim 1 or 2, wherein the groove (W) smoothly transitions to a surface of the thrust surface (S1) that is not provided with the groove (W).
10. An orbiting scroll member (60) for a scroll compressor, comprising a thrust surface (S2) for being supported by a thrust plate (40), wherein the thrust surface (S2) is formed with a groove (W) having a curved shape, the groove (W) extending radially centering on an axis of the orbiting scroll member (60), thereby enabling to improve lubrication between the thrust plate (40) and the orbiting scroll member (60).
11. An orbiting scroll member (60) according to claim 11, wherein the groove (W) is a plurality of grooves (W) arranged symmetrically.
12. An orbiting scroll member (60) according to claim 10 or 11, wherein the curve is an arc, a spiral or an involute.
13. Orbiting scroll member (60) according to claim 10 or 11, wherein the groove (W) has no common tangent with the centre circle (C) of the orbiting scroll member (60), wherein the movement trajectory of the axis of the orbiting scroll member (60) forms the centre circle (C) of the orbiting scroll member (60).
14. An orbiting scroll member (60) according to claim 10 or 11, wherein both ends of the groove (W) are provided with oil reservoirs (O) having a width larger than the width of the middle oil passage of the groove (W).
15. An orbiting scroll member (60) according to claim 10 or 11, wherein the depth of the groove (W) is equal to or less than the width of the groove (W).
16. An orbiting scroll member (60) according to claim 10 or 11, wherein the width of the groove (W) is equal to or greater than 1 mm.
17. An orbiting scroll member (60) according to claim 10 or 11, wherein the cross-sectional shape of the groove (W) is semi-circular, V-shaped or square.
18. An orbiting scroll member (60) according to claim 10 or 11, wherein the groove (W) smoothly transitions to the surface of the thrust surface (S2) where the groove (W) is not provided.
19. The orbiting scroll component (60) according to claim 10 or 11, the orbiting scroll component (60) further comprising a hub (61) and a transition (62) provided between the thrust surface (S2) and the hub (61), wherein the groove (W) extends longest from radially outside the thrust surface (S2) towards the hub (61) to a boundary of the thrust surface (S2) and the transition (62).
20. An orbiting scroll member (60) as claimed in claim 19, wherein the distance in the radial direction of both ends of the groove (W) is equal to or greater than the distance in the radial direction of the radially inner and outer sides of the thrust plate (40).
21. A scroll compressor comprising at least one of a thrust plate (40) as claimed in any one of claims 1 to 9 and an orbiting scroll member (60) as claimed in any one of claims 10 to 20.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811117545.5A CN110925194A (en) | 2018-09-20 | 2018-09-20 | Thrust plate, movable scroll member and scroll compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811117545.5A CN110925194A (en) | 2018-09-20 | 2018-09-20 | Thrust plate, movable scroll member and scroll compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN110925194A true CN110925194A (en) | 2020-03-27 |
Family
ID=69856325
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811117545.5A Pending CN110925194A (en) | 2018-09-20 | 2018-09-20 | Thrust plate, movable scroll member and scroll compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN110925194A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2021212772A1 (en) * | 2020-04-20 | 2021-10-28 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor |
| WO2022007256A1 (en) * | 2020-07-10 | 2022-01-13 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor |
| WO2024022505A1 (en) * | 2022-07-29 | 2024-02-01 | 丹佛斯（天津）有限公司 | Scroll compressor |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58113593A (en) * | 1981-12-26 | 1983-07-06 | Mitsubishi Electric Corp | Scroll compressor |
| US4734020A (en) * | 1985-12-16 | 1988-03-29 | Mitsubishi Denki Kabushiki Kaisha | Scroll type compressor with spiral oil feeding grooves in thrust bearing |
| JPH0486301A (en) * | 1990-07-30 | 1992-03-18 | Mitsubishi Heavy Ind Ltd | Scroll type fluid machine |
| JPH07189946A (en) * | 1993-12-27 | 1995-07-28 | Nippondenso Co Ltd | Lubrication structure in scroll type compressor |
| CN1955499A (en) * | 2005-10-27 | 2007-05-02 | 乐金电子(天津)电器有限公司 | Reciprocating compressor with lubrication strength thrust bearing |
| CN203035560U (en) * | 2012-12-12 | 2013-07-03 | 艾默生环境优化技术(苏州)有限公司 | Main bearing seat, movable scroll part and scroll compressor |
| CN204941960U (en) * | 2015-08-21 | 2016-01-06 | 广东美芝制冷设备有限公司 | For rotary compressor compressing mechanism and there is its rotary compressor |
| JP2017002743A (en) * | 2015-06-05 | 2017-01-05 | 富士電機株式会社 | Scroll compressor |
| CN209164081U (en) * | 2018-09-20 | 2019-07-26 | 艾默生环境优化技术(苏州)有限公司 | Thrust plate, movable scroll member and scroll compressor |
-
2018
- 2018-09-20 CN CN201811117545.5A patent/CN110925194A/en active Pending
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58113593A (en) * | 1981-12-26 | 1983-07-06 | Mitsubishi Electric Corp | Scroll compressor |
| US4734020A (en) * | 1985-12-16 | 1988-03-29 | Mitsubishi Denki Kabushiki Kaisha | Scroll type compressor with spiral oil feeding grooves in thrust bearing |
| JPH0486301A (en) * | 1990-07-30 | 1992-03-18 | Mitsubishi Heavy Ind Ltd | Scroll type fluid machine |
| JPH07189946A (en) * | 1993-12-27 | 1995-07-28 | Nippondenso Co Ltd | Lubrication structure in scroll type compressor |
| CN1955499A (en) * | 2005-10-27 | 2007-05-02 | 乐金电子(天津)电器有限公司 | Reciprocating compressor with lubrication strength thrust bearing |
| CN203035560U (en) * | 2012-12-12 | 2013-07-03 | 艾默生环境优化技术(苏州)有限公司 | Main bearing seat, movable scroll part and scroll compressor |
| JP2017002743A (en) * | 2015-06-05 | 2017-01-05 | 富士電機株式会社 | Scroll compressor |
| CN204941960U (en) * | 2015-08-21 | 2016-01-06 | 广东美芝制冷设备有限公司 | For rotary compressor compressing mechanism and there is its rotary compressor |
| CN209164081U (en) * | 2018-09-20 | 2019-07-26 | 艾默生环境优化技术(苏州)有限公司 | Thrust plate, movable scroll member and scroll compressor |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2021212772A1 (en) * | 2020-04-20 | 2021-10-28 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor |
| WO2022007256A1 (en) * | 2020-07-10 | 2022-01-13 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor |
| WO2024022505A1 (en) * | 2022-07-29 | 2024-02-01 | 丹佛斯（天津）有限公司 | Scroll compressor |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN110925194A (en) | Thrust plate, movable scroll member and scroll compressor | |
| US9243634B2 (en) | Compressor with sliding member resin layer | |
| US8152504B2 (en) | Method of operation of a spherical positive displacement rotary machine and devices for carrying out said method | |
| KR101484728B1 (en) | Scroll compressor | |
| JP2006307700A (en) | Compressor | |
| JP7075407B2 (en) | Scroll compressor | |
| US20240102482A1 (en) | Coolant Pump Having an Improved Gap Seal | |
| US9243635B2 (en) | Compressor with different resin hardness layers | |
| US9115715B2 (en) | Compressor with pressure reduction groove formed in eccentric part | |
| CN209164081U (en) | Thrust plate, movable scroll member and scroll compressor | |
| KR100496214B1 (en) | Bearing for refrigerating machine compressor and compressor | |
| CN215949828U (en) | Thrust structure of compressor and compressor | |
| CN113530827A (en) | Scroll compressor having a plurality of scroll members | |
| JP6700691B2 (en) | Electric compressor | |
| JP6618663B1 (en) | Slide bearing structure and scroll compressor | |
| CN113994096B (en) | Variable displacement lubricant pump | |
| CN107542661B (en) | Single-cylinder rotary compressor | |
| JP2008095588A (en) | Scroll compressor | |
| CN212155162U (en) | Scroll compressor having a plurality of scroll members | |
| JP2010101202A (en) | Variable displacement type compressor | |
| WO2023045968A1 (en) | Thrust structure of compressor, and compressor | |
| JP2007146705A (en) | Scroll compressor | |
| JP4706599B2 (en) | Scroll compressor | |
| JP2004190509A (en) | Gas compressor | |
| JP2020094557A (en) | Fluid machine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| CB02 | Change of applicant information | ||
| CB02 | Change of applicant information |
Address after: 215021 No.69 Suhong West Road, Suzhou Industrial Park, Jiangsu Province Applicant after: Gulun Environmental Technology (Suzhou) Co.,Ltd. Address before: 215021 No.69 Suhong West Road, Suzhou Industrial Park, Jiangsu Province Applicant before: EMERSON CLIMATE TECHNOLOGIES (SUZHOU) Co.,Ltd. |