JP2005163671A - Scroll type compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a scroll type compressor taking an appropriate value as projecting dimension of each chip seal and capable of preventing deterioration of operating performance while preventing failure of each scroll. <P>SOLUTION: In this scroll type compressor, a fixed wall body 132 and a movable wall body 142 are engaged with each other, and a movable scroll 14 is revolved while each of the chip seals 133, 143 contacts with the side face of the opposing other of the chip seals 133, 143. The minimum value of the projecting dimension of each of the chip seals 133, 143 from each of the wall bodies 132, 142 is set based on processing accuracy such as parallelism of each of the wall bodies 132, 142, assembling accuracy such as central recess amount of the movable scroll 14, and operating elements such as a load in an axial direction, wall tilting and thermal effects. The maximum value of the projecting dimension of each of the chip seals 133, 143 from each of the wall bodies 132, 142 is set based on a performance change rate. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a scroll compressor having an improved tip seal protruding dimension.

  As this type of scroll compressor, one described in patent literature is known.

  This scroll compressor includes a fixed scroll having a fixed tip seal at the tip of a spiral fixed wall body standing on one side of a fixed side plate, and a spiral movable wall body standing on one side of a movable side plate. And a movable scroll having a movable tip seal at the tip of the movable scroll, and the movable wall of the movable scroll is engaged with the fixed wall of the fixed scroll. Further, when both wall bodies are engaged, the movable chip seal of the movable wall body is in contact with one side surface of the fixed side plate, and the fixed chip seal of the fixed wall body is in contact with one side surface of the movable side plate.

When the scroll compressor is operated, the movable scroll performs a revolving orbiting motion. By this revolving and turning motion, the refrigerant is sucked between both wall bodies, and further, the sucked refrigerant moves toward the center of each scroll while being sequentially compressed, and is discharged as high-pressure refrigerant.
Japanese Utility Model Publication No. 5-66289

  By the way, during operation of the compressor, the chip seals are in sliding contact with one side surface of each scroll to prevent refrigerant leakage from the end face in the axial direction of each scroll. However, in addition to the processing accuracy of each wall and the assembly accuracy of the movable scroll, the leading edge of each wall directly presses against one side of each scroll due to the inclination of the movable scroll due to the compression load during compressor operation (so-called Galling), abnormal noise occurs, and finally each scroll is damaged.

  In order to solve such a problem, there is a method in which the tip seal is protruded greatly from the tip of each wall body. However, since the tip seal protrudes greatly, each tip portion of the wall body where the tip seal is not installed (each In the wall (from the refrigerant inlet), a large gap is formed on the front end side of each wall, resulting in a problem that a large amount of refrigerant leaks and lowers the driving performance.

  An object of the present invention is to provide a scroll compressor that takes an appropriate value as a protruding dimension of each chip seal in view of the above-described conventional problems, and can prevent deterioration of operation performance while preventing breakage of each scroll.

  In order to solve the above-described problems, the present invention provides a fixed scroll having a fixed-side tip seal at the tip of a spiral fixed wall body standing on one side of a fixed side plate, and one side of a movable side plate. A movable scroll having a movable tip seal at the tip of a spiral movable wall standing upright and engaging the fixed wall and the movable wall with each tip seal placed against one side facing each other In a scroll type compressor that revolves orbiting the movable scroll, the minimum projecting dimension of each tip seal from each wall body is the processing accuracy such as the parallelism of each wall body, and the assembly accuracy such as the center dent amount of the movable scroll And an operating element such as axial load, wall collapse, and thermal influence.

  According to the first aspect of the present invention, the minimum value of the protruding dimension of the chip seal is determined in consideration of operating factors such as axial load, wall collapse, and thermal influence in addition to the processing accuracy and the assembly accuracy. Thereby, the galling of each scroll can be prevented.

  According to a second aspect of the present invention, there is provided a fixed scroll having a fixed side tip seal at the tip of a spiral fixed wall body standing on one side of the fixed side plate, and a spiral movable wall body standing on one side of the movable side plate. Scroll-type compression, which has a movable scroll having a movable side tip seal at the tip of the shaft, and revolves the movable scroll in a state in which the fixed wall body and the movable wall body are engaged with each tip seal against one side surface facing each other. In the machine, the maximum value of the projecting dimension of each tip seal from each wall is set based on the performance change rate.

  According to the second aspect of the present invention, the maximum value of the protruding dimension is determined based on the permissible value of the maximum value of the protruding dimension as the performance change rate of the refrigeration capacity, for example, the performance change rate. Thereby, the remarkable fall of driving performance can be prevented.

  The invention of claim 3 has a structure in which both the minimum value of claim 1 and the maximum value of claim 2 are set, and can realize both galling prevention and performance deterioration prevention.

  The minimum value may be 70 μm and the maximum value may be 180 μm.

  ADVANTAGE OF THE INVENTION According to this invention, breakage of each scroll of a scroll compressor can be prevented, and the remarkable fall of driving performance can be prevented.

  1 to 4 show an embodiment of a scroll compressor according to the present invention, FIG. 1 is a cross-sectional view of the scroll compressor, and FIG. 2 is a plan view showing a meshed state of a fixed scroll and a movable scroll. FIG. 3 is a cross-sectional view showing how the fixed scroll and the movable scroll are engaged, and FIG. 4 is a graph showing the relationship between the refrigeration capacity and the tip seal protrusion amount.

  First, the schematic structure of the scroll compressor will be described with reference to FIGS. 1 and 2. The scroll compressor 1 has a rear housing 11 and a front housing 12 joined so as to close the opening of the rear housing 11. A fixed scroll 13 and a movable scroll 14 are installed inside the rear housing 11. A scroll revolution mechanism 15 is installed inside the front housing 12, and an electromagnetic clutch 16 is installed outside the front housing 12.

  As shown in FIG. 2, the fixed crawl 13 includes a disk-shaped fixed side plate 131 and a spiral fixed wall body 132 erected from one side 131 a of the fixed side plate 131. Here, as shown in FIG. 1, a refrigerant discharge chamber 111 is provided between the other side surface of the fixed side plate 131 and the bottom of the rear housing 11. In addition, a discharge port 131b passes through the fixed side plate 131, and a discharge valve 131c that opens and closes the discharge port 131b is installed on the discharge chamber 11 side, and the refrigerant compressed on the center side of the fixed wall 132 is discharged. It is discharged into the discharge chamber 111 through the outlet 131b. Further, as shown in FIG. 2, a spiral fixed-side tip seal 133 is fitted at the tip of the fixed wall 132.

  The movable scroll 14 includes a disk-shaped movable side plate 141 and a spiral movable wall body 142 erected from one side surface 141 a of the movable side plate 141. As shown in FIG. 2, the movable wall body 142 is disposed so as to mesh with the fixed wall body 132 of the fixed scroll 13, and a compression space is formed between the fixed wall body 132 and the movable wall body 142. Further, as shown in FIG. 2, a spiral movable side tip seal 143 is fitted at the tip of the movable wall 142. Although not shown, a refrigerant suction port is provided outside the movable wall 142 so that the refrigerant is guided from the outer peripheral side of each wall 132, 142 to the inside of each wall 132, 142.

  The scroll revolving mechanism 15 is fixed to a drive bush 152 to which a counterweight 151 is fixed, a crank 154 connected to the drive bush 152 via an eccentric pin 153, a main shaft 155 connected to the crank 154, and a tip end side of the main shaft 155. Hub 156. The drive bush 152 is fitted into the other side surface of the movable side wall 141 via a bearing 156a. Here, when the main shaft 155 rotates, the rotational force is transmitted to the drive bush 152 through the crank 154 and the eccentric pin 153, and the movable scroll 14 performs a revolving motion. Reference numeral 157 denotes a rotation regulating member that regulates the rotation of the movable scroll 14.

  The electromagnetic clutch 16 includes an electromagnetic coil 162 wound around an annular rotor 161, an armature plate 163 that can be attracted to the rotor 161, and a leaf spring 164 that connects the hub 156 and the armature plate 163. A bearing 165 is interposed between the rotor 161 of the electromagnetic clutch 16 and the front housing 12 to support the rotor 161 rotatably. Further, the rotational force of an automobile engine (not shown) is transmitted to the outer surface of the rotor 161 by a belt (not shown), and the rotor 161 is always rotating. Here, when the electromagnetic coil 162 is energized, the rotor 161 is magnetized and the armature plate 163 is attracted to the rotor 161. As a result, the armature plate 163 rotates, and the rotational force of the armature 163 is transmitted to the main shaft 155 through the plate spring 164 and the hub 156.

  The above-described configuration is the same in the conventional scroll compressor. The refrigerant is sucked between the wall bodies 132 and 142 by the revolving motion of the movable scroll 14, and further compressed by the wall bodies 132 and 142. The space is sequentially reduced to increase the pressure of the refrigerant.

  The feature of the scroll compressor 1 according to the present invention is that the protruding dimensions of the tip seals 133 and 143 are improved.

  Here, as shown in FIG. 3, the protruding dimensions of the chip seals 133 and 143 refer to the protruding amount W of the chip seals 133 and 143 protruding from the front end surfaces of the wall bodies 132 and 142. The value refers to the allowable minimum value of the protrusion amount W, and the minimum value of the protrusion dimension refers to the allowable maximum value of the protrusion amount W.

  First, the minimum value of the protrusion dimension will be described. In setting this minimum value, attention is paid to the cause of galling of the walls 132 and 142, which is a conventional problem. The first cause of galling is in the machining accuracy of parts. That is, the end surfaces of the walls 132 and 142 must be processed so as to be completely flush with each other, but a tolerance of +60 μm is required for the processing accuracy (parallelism of the walls 132 and 142).

  Second is the assembly accuracy of the parts. That is, when assembling the movable scroll 14 to the fixed scroll 13, each chip seal 133, 143 must be assembled in contact with each side surface 131 a, 141 a, but when assembling the movable scroll 14, the center side is slightly depressed, Due to its assembling accuracy, it is separated from the side surface 131a of the wall 132 by about 10 μm.

  Third, there is an error due to the operation of the movable scroll 144. In other words, since a compressive reaction force is applied to the movable scroll 14 when the refrigerant is compressed, a load is applied in the axial direction of the movable scroll 14 (axial load). Further, since the movable scroll 14 is supported in a cantilevered state with respect to the scroll revolution mechanism 15, the movable scroll 14 may tilt in the radial direction during operation (so-called wall collapse; indicated by a two-dot chain line in FIG. 3). Furthermore, each wall body 132,142 is thermally expanded by the heat which generate | occur | produces at the time of refrigerant | coolant compression (thermal influence). When these clearance changes during operation are combined, each wall body 132, 142 has a protruding change of 20 μm.

From the above points, if the minimum value of the protruding dimension of each chip seal 133, 143 is calculated,
(60 μm + 20 μm) −10 μm = 70 μm
Therefore, 70 μm is obtained as the minimum value of the protruding dimensions of the tip seals 133 and 143.

  Next, the maximum value of the protrusion dimension will be described. By the way, the chip seals 133 and 143 are not provided on the entire walls 132 and 142, but, as shown in FIG. The tip seals 133 and 143 are not provided on the portions 132a and 142a. Therefore, when the projecting dimensions of the tip seals 133 and 143 are excessively increased in order to prevent so-called galling, refrigerant leakage from the portions 132a and 142a becomes excessive, and the operation performance of the scroll compressor 1 is significantly deteriorated.

Therefore, as shown in FIG. 4, a performance change approximation line was taken from the relationship between the refrigeration capacity and the tip seal protrusion amount, and the maximum value was obtained by setting the performance change rate at which the performance change is allowed, 5%. Accordingly, it has been found that it is optimal to set the maximum protrusion dimension of the tip seals 133 and 143 to 180 μm. Therefore, in the scroll compressor 1 according to the present embodiment, as shown in FIG.
70 μm <W <180 μm
When setting with, optimal operation will be performed.

  The protruding dimensions of the tip seals 133 and 143 can be easily adjusted by changing the depth of the groove in which the tip seals 133 and 143 are inserted, or by managing the thickness dimensions of the tip seals 133 and 143. it can. Further, as a means for satisfying this dimensional range, a special processing technique and strict component accuracy are not required.

  Although not shown, the tip of each wall body may be processed with a stepped groove, and a chip seal may be installed in the stepped groove. However, the tip seal protrusion amount may be set within the same range as in the above embodiment. .

Cross section of scroll compressor Top view showing how fixed and movable scrolls are engaged Enlarged sectional view showing how the fixed scroll and movable scroll are engaged Graph showing the relationship between refrigeration capacity and tip seal protrusion

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Scroll type compressor, 13 ... Fixed scroll, 14 ... Movable scroll, 131 ... Fixed side plate, 132 ... Fixed wall body, 133 ... Fixed side chip seal, 141 ... Movable side plate, 142 ... Movable wall body, 143 ... Movable side Tip seal.

Claims (6)

A fixed scroll having a fixed tip seal at the tip of a spiral fixed wall standing upright on one side of the fixed side plate, and a movable tip seal at the tip of a spiral movable wall standing up one side of the movable side plate A scroll compressor that revolves the movable scroll in a state in which the fixed wall body and the movable wall body are engaged with each other and the tip seals are in contact with one side surface facing each other.
The minimum value of the projecting dimension of each tip seal from each wall body, the processing accuracy such as the parallelism of each wall body, the assembly accuracy such as the center dent amount of the movable scroll, the axial load, wall collapse and A scroll compressor that is set based on operating factors such as thermal effects. A fixed scroll having a fixed tip seal at the tip of a spiral fixed wall standing upright on one side of the fixed side plate, and a movable tip seal at the tip of a spiral movable wall standing up one side of the movable side plate A scroll compressor that revolves the movable scroll in a state in which the fixed wall body and the movable wall body are engaged with each other and the tip seals are in contact with one side surface facing each other.
A scroll compressor, wherein a maximum value of a protruding dimension of each tip seal from each wall is set based on a performance change rate. A fixed scroll having a fixed tip seal at the tip of a spiral fixed wall standing upright on one side of the fixed side plate, and a movable tip seal at the tip of a spiral movable wall standing up one side of the movable side plate A scroll compressor that revolves the movable scroll in a state in which the fixed wall body and the movable wall body are engaged with each other and the tip seals are in contact with one side surface facing each other.
The minimum value of the projecting dimension of each tip seal from each wall body, the processing accuracy such as the parallelism of each wall body, the assembly accuracy such as the center dent amount of the movable scroll, the axial load, wall collapse and A scroll compressor characterized in that it is set on the basis of operating factors such as thermal influence and the maximum value of the projecting dimension of each tip seal from each wall is set on the basis of the rate of change in performance. The scroll compressor according to claim 1 or 3, wherein a minimum value of the projecting dimension is set to 70 µm. The scroll compressor according to claim 2 or 3, wherein a maximum value of the projecting dimension is set to 180 µm. The scroll compressor according to claim 3, wherein the minimum value of the protruding dimension is set to 70 µm, and the maximum value of the protruding dimension is set to 180 µm.

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