JP2015028310A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To automatically adjust a position of a turning scroll stably by a simple constitution, and to surely maintain a sealing property of a compression chamber while avoiding contact between a scroll end and a confronting surface.SOLUTION: A compression chamber 8 is formed by a fixed scroll 1 and a floating scroll 2 supported by a support frame 3, and the compression chamber moves with reducing the capacity by revolution of the floating scroll so as to compress gas. A protrusion wall 25 protruding toward a pedestal 15 of the supporting frame is provided on a peripheral edge of a movable substrate 6 of the floating scroll, the protrusion wall surrounds a space between the movable substrate and the pedestal, and thus, a compression chamber 23 is formed, and a pressure introduction passage 20 for introducing a part of the compressed gas is provided. A distance between the fixed scroll and the pedestal is set so that the floating scroll is movable in a vertical direction, and the pressure chamber communicates with an area outside the protrusion wall through a space formed between an end surface of the protrusion wall and the pedestal. A labyrinth groove 26 extended in a circumferential direction is provided on the end surface of the protrusion wall.

Description

  The present invention relates to a scroll compressor suitable for compression to a high gas pressure, and more particularly to an improvement for improving the durability of a sealing surface between a fixed scroll and a turning scroll.

  The scroll compressor is configured by meshing a spiral blade provided on the fixed scroll and a spiral blade provided on the orbiting scroll. The fixed scroll and the orbiting scroll are held by the support frame so that the orbiting scroll is movable. Due to the revolution of the orbiting scroll, the compression chamber formed between the spiral blades of both scrolls moves while reducing the volume, thereby compressing the gas.

  Incidentally, for example, in a compressor for compressing carbon dioxide used as a refrigerant in a refrigeration cycle, the discharge pressure of carbon dioxide is very high. Therefore, in the scroll compressor, a very large thrust load based on the pressure in the compression chamber acts on the orbiting scroll. Therefore, the orbiting scroll substrate is strongly biased toward the support frame.

  For example, Patent Literature 1 discloses a technique for buffering a thrust load due to compression to such a high pressure. In the scroll compressor described in FIG. 1 of Patent Document 1, a back pressure chamber is formed between the back side of the orbiting scroll and the fixed wall surface of the housing. An annular seal housing groove is provided on the outer periphery on the back side of the orbiting scroll member, and a chip seal is inserted. The tip seal is slidable and resiliently abutted against the fixed wall surface (paragraph 0042 of Patent Document 1). Therefore, a generally sealed space is formed between the back surface of the orbiting scroll member and the fixed wall surface by the sealing action by the tip seal. However, the seal function lowering portion is configured by separating a part of the tip seal in the circumferential direction. In this space, the high pressure of the compression chamber is introduced through the introduction passage and functions as a back pressure chamber. Further, this back pressure chamber is connected to the low pressure region through the seal function lowering portion.

  When the pressure in the compression chamber rises due to the start of the operation of the scroll compressor, an urging force in a direction away from the fixed scroll member acts on the orbiting scroll member due to the high pressure in the compression chamber. On the other hand, since the high-pressure gas in the compression chamber is introduced into the back pressure chamber, a biasing force toward the fixed scroll member acts on the orbiting scroll member due to the pressure in the back pressure chamber. At this time, the gas is led out to the low pressure region through the seal function lowering portion, so that the pressure in the back pressure chamber is adjusted.

  By these actions, the relative position of the orbiting scroll member with respect to the fixed wall is automatically set according to the balance between the force based on the pressure in the compression chamber and the force based on the pressure in the back pressure chamber. Thereby, the thrust load which acts on the orbiting scroll member due to the pressure in the compression chamber is buffered, and the sliding resistance with the fixed wall can be reduced.

  The seal function lowering portion provided in the tip seal is an element for improving the function of adjusting the pressure in the back pressure chamber in the scroll compressor disclosed in Patent Document 2. That is, Patent Document 2 adopts a configuration in which the entire gap between the orbiting scroll member and the fixed wall is used as a gas outlet passage from the back pressure chamber to the low pressure region. In this case, in order to adjust the pressure in the back pressure chamber with high accuracy, it is necessary to process each facing surface of the orbiting scroll member and the fixed wall with high accuracy, which causes an increase in manufacturing cost. Instead of this configuration, by providing a sealing function lowering portion to serve as a gas outlet passage, it is possible to suitably adjust the pressure of the back pressure chamber at low cost without requiring high-precision processing.

JP 2004-204680 A Japanese Unexamined Patent Publication No. 2000-249086

  In the configuration disclosed in Patent Document 1, as described above, the gap between the orbiting scroll member around the back pressure chamber and the fixed wall is blocked by the tip seal. For this purpose, the tip seal is slidable and resiliently abutted against the end face of the fixed wall. Accordingly, the tip seal is worn with the operation of the scroll compressor, which greatly affects the durability of the compressor.

  Further, as in the configuration disclosed in Patent Document 2, when the entire gap between the orbiting scroll member and the fixed wall is used as a gas outlet passage from the back pressure chamber to the low pressure region, the back pressure chamber is appropriately set. In order to function, not only high processing accuracy is required as described above, but also there is a problem that the effect of adjusting the pressure in the back pressure chamber cannot be obtained sufficiently. That is, when a simple gap around the back pressure chamber is used as the gas outlet passage, the pressure in the back pressure chamber does not increase sufficiently even if the gap becomes considerably small, and the orbiting scroll The effect of adjusting the position of the member cannot be obtained sufficiently.

  Accordingly, the present invention provides a scroll compression in which the position of the orbiting scroll is stably and appropriately automatically adjusted with a simple configuration, and the sealing performance of the compression chamber is reliably maintained while avoiding contact between the scroll tip and the opposed surface. The purpose is to provide a machine.

  The scroll compressor according to the present invention includes a fixed scroll having a configuration in which a first spiral blade is provided on a lower surface of a fixed substrate, a floating scroll having a configuration in which a second spiral blade is provided on an upper surface of a movable substrate, An eccentric drive element for revolving the floating scroll is disposed, and the support coupled to the fixed substrate is interposed between the pedestal portion and the fixed scroll so that the floating scroll can revolve. And a frame. The first and second spiral blades are meshed with each other to form a compression chamber, and the compression chamber moves while reducing its volume due to the revolution of the floating scroll to compress the gas.

  In order to solve the above-mentioned problem, the scroll compressor according to the present invention is provided with a projecting wall projecting toward the pedestal portion at a peripheral portion of the movable substrate, and the gap between the movable substrate and the pedestal portion is defined as the gap. A pressure chamber is formed by surrounding the protruding wall, and a pressure introduction path for introducing a part of the gas compressed in the compression chamber into the pressure chamber is provided, and an interval between the fixed scroll and the base portion is The floating scroll is set to be movable within a predetermined range in the vertical direction, and the pressure chamber communicates with a low-pressure region outside the projection wall through a gap formed between a tip surface of the projection wall and the pedestal portion. The labyrinth seal is formed by providing a labyrinth groove extending in the circumferential direction on the tip surface of the projection wall.

  According to the scroll compressor having the above configuration, the position of the floating scroll is automatically adjusted with respect to the fixed scroll and the pedestal portion by the action of the pressure chamber. This action has practically sufficient stability due to the labyrinth seal. This is because a sufficient back pressure can be obtained by the orifice effect of the labyrinth seal, and when the gap formed between the tip surface of the projection wall and the upper surface of the pedestal portion decreases, the pressure in the pressure chamber increases rapidly. . As a result, the sealing performance of the compression chamber is securely maintained while avoiding contact between the scroll tip and the opposing surface, and the tip seal is unnecessary, eliminating the effects of tip seal wear and improving the durability of the device. Can be made.

Sectional drawing which shows the scroll compressor in Embodiment 1 Sectional drawing along the AA line in FIG. 1 of the scroll compressor Sectional drawing of the support frame 3 which comprises the scroll compressor Plan view of the support frame 3 Sectional drawing of the floating scroll 2 which comprises the scroll compressor Bottom view of the floating scroll 2 The eccentric shaft 28 which comprises the scroll compressor is shown, (a) is a front view, (b) is a top view Sectional drawing along the BB line in FIG. 1 of the scroll compressor 1 is a bottom view of the scroll compressor as seen from the spindle bearing holder 42 side in FIG. Sectional drawing which expands and shows the structure around the pressure chamber 23 and the labyrinth seal 27 shown in FIG. 1 of the scroll compressor Sectional drawing which shows the scroll compressor in Embodiment 2. Sectional drawing along CC line in FIG. 12 of the scroll compressor

  The scroll compressor of the present invention can take the following aspects based on the above configuration.

  That is, the front end surface of the first spiral blade and the upper surface of the movable substrate, and the front end surface of the second spiral blade and the lower surface of the fixed substrate are directly facing each other without interposing other elements. To do. This eliminates the need for a tip seal, which is advantageous for improving wear resistance and reducing manufacturing costs with a simple structure.

  The eccentric drive element is provided with an eccentric shaft that is rotatably mounted on the pedestal portion and faces the lower surface of the movable substrate, and an upper end surface portion of the eccentric shaft is eccentric with respect to a rotation axis of the eccentric shaft. A circular eccentric recess having a central axis at a position is provided, an engagement shaft extending toward the base portion is provided on the lower surface of the movable substrate, and the engagement shaft is mounted in the eccentric recess of the eccentric shaft. The floating scroll is revolved and driven by the rotation of the eccentric shaft through the engagement between the eccentric recess and the engagement shaft. According to this configuration, the lower surface of the movable substrate only occupies a region where the engagement axis is small, and a sufficiently large area can be secured as a region for providing the pressure chamber on the lower surface of the movable substrate. Due to the large area of the pressure chamber, a high pressure can be stably maintained, the change in the pressure balance between the compression chamber and the pressure chamber is stable, and the position adjustment of the floating scroll operates stably.

  Further, a pair of the engagement shafts may be provided and arranged on opposite sides with respect to the center axis of the revolution. Thereby, the rotation prevention effect of the floating scroll can be obtained with a simple configuration.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

<Embodiment 1>
1 is a cross-sectional view showing a scroll compressor according to Embodiment 1. FIG. FIG. 2 shows a cross-sectional view along the line AA in FIG. This scroll compressor has a structure in which a fixed scroll 1 made of, for example, an aluminum alloy and a floating scroll 2 are combined and held by a support frame 3.

  The fixed scroll 1 is configured by providing the first spiral blade 5 on the lower surface of the fixed substrate 4, and the floating scroll 2 is configured by providing the second spiral blade 7 on the upper surface of the movable substrate 6. The first and second spiral blades 5 and 7 have a planar shape shown in FIG. An outer peripheral end of the first spiral blade 5 is connected to a cylindrical outer peripheral wall 5a that surrounds the first spiral blade 5, and a spiral closed space is formed. The mutual arrangement of the floating scroll 2 and the fixed scroll 1 is set so that the second spiral blade 7 is engaged with the spiral closed space. The compression chamber 8 is formed in the spiral closed space by meshing the first spiral blade 5 and the second spiral blade 7. The compression chamber 8 moves while reducing the volume by the revolution of the floating scroll 2, and the gas in the compression chamber 8 is compressed.

  In the compression chamber 8 at the center of the fixed scroll 1, a discharge passage vertical portion 9 that extends vertically upward in the fixed substrate 4 is opened. The discharge path vertical portion 9 communicates with a discharge path horizontal portion 10 extending in the horizontal direction in the fixed substrate 4. As shown in FIG. 2, the discharge path horizontal portion 10 is opened at the peripheral edge of the fixed substrate 4 and is provided with a discharge port 11. From the discharge port 11, the gas compressed in the compression chamber 8 is supplied to the outside.

  Although only shown in FIG. 2, a suction passage vertical portion 12 extending vertically upward in the fixed substrate 4 is formed at the outer peripheral end portion of the spiral closed space formed by the first spiral blade 5 and the cylindrical outer peripheral wall 5 a. It is open. The suction passage vertical portion 12 communicates with a suction passage horizontal portion 13 extending in the horizontal direction in the fixed substrate 4. The suction path horizontal portion 13 opens at the peripheral edge of the fixed substrate 4 and is provided with a suction port 14. The suction port 14 is supplied with a gas to be compressed, such as air.

  The support frame 3 includes a pedestal portion 15, an upper cylindrical portion 16 that extends to the upper portion, and a lower cylindrical portion 17 that extends to the lower portion. The floating scroll 2 is held on a pedestal portion 15 so as to be capable of revolving, and the upper end portion of the upper cylindrical portion 16 is coupled to the fixed substrate 4. The cross-sectional shape of the support frame 3 is shown in FIG. 3, and the planar shape is shown in FIG. A fitting inner peripheral surface 18 is formed inside the upper cylindrical portion 16, and a cylindrical outer peripheral wall 5 a that protrudes downward from the fixed substrate 4 of the fixed scroll 1 is fitted. The pedestal portion 15 is provided with a pair of drive holes 19. Elements for revolving the floating scroll 2 are arranged in the drive hole 19 (described later), and circular holes having various diameters corresponding to each element are included. The arrangement of the pair of drive holes 19 is set on the opposite side with respect to the center axis of revolution of the floating scroll 2. A mechanism for transmitting a driving force to the elements arranged in the drive hole 19 is arranged in the lower cylindrical portion 17 (described later).

  In the center of the pedestal portion 15, a pressure introduction path vertical portion 20 that extends vertically downward is opened. The pressure introduction path vertical portion 20 communicates with the pressure introduction path horizontal portion 21 extending in the horizontal direction in the pedestal portion 15. The pressure introduction path horizontal portion 21 opens at the peripheral edge of the pedestal portion 15 and is provided with a pressure introduction port 22. Although not shown, the pressure introduction port 22 is connected to the discharge port 11 of the fixed scroll 1 and a part of the gas compressed in the compression chamber 8 is introduced.

  As shown in FIG. 1, a gap is provided between the lower surface of the movable substrate 6 and the upper surface of the pedestal portion 15 to form a pressure chamber 23. The cross-sectional shape of the floating scroll 2 is shown in FIG. 5, and the bottom surface shape is shown in FIG. A pair of engagement shafts 24 extending toward the pedestal portion 15 are provided on the lower surface of the movable substrate 6. A protrusion wall 25 is provided on the peripheral edge of the lower surface of the movable substrate 6, surrounds the pressure chamber 23, and protrudes toward the pedestal portion 15. A labyrinth groove 27 extending in the circumferential direction is provided on the distal end surface (lower end surface) of the protruding wall 25 to form a labyrinth seal 27. The feature of this embodiment is that the labyrinth seal 27 is provided, and details thereof will be described later.

  As shown in FIG. 1, an eccentric shaft 28 is attached to the drive hole 19 of the base portion 15. FIG. 7A shows a front view of the eccentric shaft 28 and FIG. 7B shows a plan view thereof. The eccentric shaft 28 includes a rotating shaft 29 and an upper end large diameter portion 30. The upper end large diameter portion 30 is provided with a substantially circular eccentric recess 31 having a central axis at a position eccentric with respect to the rotation shaft 29. As shown in FIG. 1, the engagement shaft 24 of the floating scroll 2 is mounted in the eccentric recess 31.

  As shown in FIGS. 3 and 4, the drive hole 19 includes a bearing mounting portion 32 that is the uppermost maximum diameter region, a large-diameter portion housing portion 33, a leap seal mounting portion 34, and a shaft insertion hole 35. Become. FIG. 1 is a sectional view showing a state in which each element is mounted in the drive hole 19, and FIG. 8 shows the planar shape as a sectional view taken along the line BB in FIG. 1.

  As can be seen from FIGS. 1, 3, 4, and 8, the bearing mounting portion 32 is fitted with the upper end large diameter portion 30 of the eccentric shaft 28 via the large diameter portion bearing 36. Thereby, the eccentric shaft 28 is rotatably supported. A portion of the upper end large diameter portion 30 that protrudes below the large diameter portion bearing 36 is accommodated in the large diameter portion accommodating portion 33. A rotating shaft 29 of the eccentric shaft 28 is fitted in the leap seal mounting portion 34 via a leap seal 37. Thereby, the drive hole 19 is sealed with respect to the lower part of the base part 15. A swing bearing 39 is mounted in the eccentric recess 31 of the eccentric shaft 28 via a bush 38, and the engagement shaft 24 of the movable substrate 6 is fitted in the swing bearing 39. Thereby, the eccentric shaft 28 becomes rotatable in a state where the engagement shaft 24 is fitted. A slight gap 31 a is formed between the inner peripheral surface of the eccentric recess 31 and the outer peripheral surface of the bush 38.

  A lower frame 40 is attached to the lower end of the lower cylindrical portion 17 of the support frame 3, and supports the lower end of the rotary shaft 29 via a bearing 41. A main shaft bearing holder 42 is attached to the lower portion of the lower frame 40 to hold the drive shaft 43 rotatably, and its upper end portion extends vertically in the lower cylindrical portion 17. The lower end portion of the drive shaft 43 extends below the main shaft bearing holder 42 and is rotationally driven by a motor (not shown). A gear 44 is attached to each of the pair of rotating shafts 29 and meshes with a gear (not shown in FIG. 1) attached to the drive shaft 43.

  FIG. 9 is a bottom view of the relationship between the rotary shaft 29 and the drive shaft 43 and the gears as viewed from the spindle bearing holder 42 side in FIG. The gear 45 attached to the drive shaft 43 is meshed with each gear 44 attached to the pair of rotating shafts 29. Thereby, the rotation of the drive shaft 43 is simultaneously transmitted to the pair of rotating shafts 29, and the pair of eccentric shafts 28 are simultaneously rotationally driven in the same direction.

  The operation of the scroll compressor having the above configuration is as follows. That is, the rotation of the motor is transmitted through the drive shaft 43, and the eccentric shaft 28 is rotationally driven in the same direction. Thereby, the engagement shaft 24 revolves around the axis of the rotation shaft 29 in the eccentric recess 31 through the engagement with the swivel bearing 39. As the pair of engagement shafts 24 revolve in the same manner, the floating scroll 2 is driven to revolve. At that time, the rotation of the floating scroll 2 is prevented by the pair of engaging shafts 24. Therefore, in this configuration, a rotation prevention mechanism is not necessary. The revolving motion of the floating scroll 2 compresses the gas in the compression chamber 8 based on the action of a known scroll compressor.

  The compressed high-pressure gas is supplied to the outside from the discharge port 11, and a part of the compressed high-pressure gas is supplied to the pressure chamber 23 via the pressure introduction port 22, and the pressure in the pressure chamber 23 increases. Due to the pressure in the pressure chamber 23, a biasing force directed toward the fixed scroll 1 acts on the floating scroll 2. A force based on the pressure in the compression chamber 8 acts on the floating scroll 2 in a direction away from the fixed scroll 1. Therefore, the relative position of the floating scroll 2 with respect to the pedestal portion 15 is determined according to the balance of both forces.

  The structure around the pressure chamber 23 and the labyrinth seal 27 and the operation thereof for appropriately performing the above operation will be described with reference to FIGS. FIG. 10 is an enlarged cross-sectional view showing the structure around the pressure chamber 23 and the labyrinth seal 27 shown in FIG. A space for holding the floating scroll 2 formed between the fixed scroll 1 and the support frame 3 has a margin for enabling the floating scroll 2 to turn (revolve) in the horizontal direction. That is, as shown in FIG. 1, a lateral gap 46 having a dimension corresponding to the turning range is set between the inner peripheral surface of the upper cylindrical portion 16 and the outer peripheral surface of the movable substrate 6.

  Also in the vertical direction, there is a margin that allows the floating scroll 2 to be displaced within a predetermined range. That is, as shown in FIG. 10, the vertical gap 47 is set between the fixed scroll 1 and the pedestal 15. As a result, a gap that allows the pressure chamber 23 to communicate with the low-pressure region outside the projection wall 25 can be formed between the distal end surface of the projection wall 25 and the upper surface of the pedestal portion 15. As a result, the pressure chamber 23 and the labyrinth seal 27 function effectively to appropriately adjust the vertical position of the floating scroll 2.

  The high-pressure compressed gas introduced from the compression chamber 8 through the pressure introduction port 22 of the pedestal portion 15 is supplied to the upper surface of the pedestal portion 15 via the pressure introduction path vertical portion 20 as can be seen from FIGS. Then, the pressure chamber 23 is filled. When the floating scroll 2 receives an upward force due to the gas pressure acting on the lower surface of the movable substrate 6, a gap (hereinafter referred to as “projection wall front end gap”) is formed between the front end surface of the projection wall 25 and the upper surface of the base portion 15. Are formed). As a result, the pressure chamber 23 communicates with the outer low pressure region through the labyrinth seal 27 and the gas is discharged. Accordingly, the gas pressure in the pressure chamber 23 is adjusted according to the distance between the labyrinth seal 27 and the upper surface of the pedestal 15.

  On the other hand, a biasing force acting in a direction away from the fixed scroll 1 (downward) is applied to the floating scroll 2 due to the high pressure in the compression chamber 8. This urging force displaces the floating scroll 2 in the direction in which the gap between the protrusion wall tips decreases. Eventually, the relative position of the floating scroll 2 with respect to the pedestal 15 and the fixed scroll 1 is automatically adjusted according to the balance between the force based on the pressure in the compression chamber 8 and the force based on the pressure in the pressure chamber 23.

  By such automatic adjustment of the position of the floating scroll 2, the gap between the scroll tip, that is, the gap between the tip of the first and second spiral blades 5, 7 and the upper surface of the movable substrate 6 and the lower surface of the fixed substrate 4. Is set to the optimum state. By appropriately setting the gap, sufficient sealing performance of the compression chamber 8 can be ensured without using a tip seal, and the movable substrate 6 and the fixed substrate at the tips of the first and second spiral blades 5 and 7 can be secured. The effect of buffering the influence of sliding on 4 is obtained. In addition, an effect of buffering the influence of sliding between the movable substrate 6 and the pedestal portion 15 can be obtained against the thrust load due to the high pressure in the compression chamber 8 with respect to the floating scroll 2 without using a seal member. This is suitable as an oil-free configuration and has a high noise reduction effect.

  The action of automatically adjusting the position of the floating scroll 2 by the pressure chamber 23 as described above has practically sufficient stability by providing the labyrinth seal 27. This is because a sufficient back pressure can be obtained due to the orifice effect of the labyrinth seal 27, and the change in the pressure in the pressure chamber 23 becomes curved with respect to the change in the size of the protrusion wall tip gap. . That is, the pressure in the pressure chamber 23 rapidly increases as the protrusion wall tip clearance decreases. As a result, an action sufficient to buffer the thrust load due to the high pressure in the compression chamber 8 with respect to the floating scroll 2 is obtained, and the automatic adjustment of the position of the floating scroll 2 is stabilized.

  On the other hand, when the labyrinth seal 27 is not used, that is, when the labyrinth groove 26 is not provided in the tip surface of the projection wall 25 and is flat, the pressure against the change in the size of the projection wall tip gap is The change in pressure in the chamber 23 is substantially linear. Therefore, even when the gap between the protrusion wall tips is reduced, the pressure in the pressure chamber 23 does not increase rapidly, and the pressure in the pressure chamber 23 is sufficiently high to resist the high pressure in the compression chamber 8. It is difficult to obtain. For this reason, the action of automatically adjusting the position of the floating scroll 2 by the pressure chamber 23 cannot be practically sufficiently stable.

  Also, due to the effect of using the labyrinth seal 27, unlike Patent Document 1, it is not necessary to arrange a seal member that slides around the back pressure chamber, so that the durability of the device due to wear of the seal member is reduced. Decrease can be avoided.

  In addition, the operation of the labyrinth seal 27 can ensure high reliability even if the processing accuracy of each part is low. That is, the accuracy of the projection wall tip clearance is determined by the processing accuracy of the tip surface of the projection wall 25 and the upper surface of the pedestal 15, but the operation of the labyrinth seal 27 is less affected by the accuracy of the projection wall tip clearance. Therefore, it is effective in reducing the product cost, together with the fact that no seal member is required and the number of parts can be suppressed.

  In order to surely obtain the effect of the labyrinth seal 27 as described above, it is advantageous to configure the mechanism for revolving the floating scroll 2 by transmitting the rotation of the eccentric shaft 28 as described above. That is, a simple engagement shaft 24 is protruded from the lower portion of the movable substrate 6 and engaged with the eccentric recess 31 (forming the boss portion) of the eccentric shaft 28, and the rotation is transmitted through the engagement. is there. According to this configuration, as shown in FIG. 6, the engagement shaft 24 only occupies a small region on the lower surface of the movable substrate 6. This is because the slewing bearing 39 is held by the eccentric recess 31. Therefore, a sufficiently large area can be secured as a region for providing the pressure chamber 23 on the lower surface of the movable substrate 6.

  Since the area of the pressure chamber 23 is large, the amount of gas filling is sufficiently large, and a high pressure can be stably maintained. As a result, the change in the pressure balance between the compression chamber 8 and the pressure chamber 23 due to the gas passing through the labyrinth seal 27 becomes stable, and the position adjustment of the floating scroll 2 operates stably. According to the configuration of the present embodiment, since the pressure chamber 23 can be configured with a sufficient area even in the case of a small scroll compressor, the above-described effect becomes particularly significant.

  On the other hand, in the configuration disclosed in Patent Document 1 or 2, for example, a boss portion protrudes from the lower surface of the movable substrate, and an eccentric shaft that transmits rotational driving force is interposed in the boss portion via a bearing and a bush. It is mated. That is, since a plurality of elements are mounted in the boss portion, the lower surface of the movable substrate occupies a large proportion. As a result, this is an obstacle to ensuring a sufficient area for providing the pressure chamber.

  Further, as in the present embodiment, the floating scroll 2 can be lightened by providing only the engagement shaft 24 on the lower surface of the movable substrate 6. Therefore, the responsiveness of the vertical position adjustment of the floating scroll 2 is good, and it is advantageous for stably obtaining the operation of adjusting the position of the floating scroll 2 as described above.

<Embodiment 2>
FIG. 11 is a cross-sectional view showing the scroll compressor according to the second embodiment. FIG. 12 shows a cross-sectional view along the line CC in FIG. The basic features of this scroll compressor are the same as in the first embodiment. In the present embodiment, the configuration using the pair of engagement shafts 24 and the eccentric shaft 28 in the first embodiment is changed to a configuration using a single engagement shaft and an eccentric shaft. Therefore, the same reference numerals are given to the same components as those in the first embodiment, and the description will be simplified.

  In FIG. 11, the structure of the fixed scroll 1 and the structure of the second spiral blade 7 of the floating scroll 48 are the same as those in the first embodiment. The structure of the movable substrate 49 of the floating scroll 48 and the structure of the support frame 50 are different from those of the first embodiment. A single engagement shaft 51 is provided on the lower surface of the movable substrate 49. A pressure chamber 53 is formed around the engaging shaft 51 of the movable substrate 49 with the pedestal portion 52 of the support frame 50, and the periphery thereof is surrounded by a labyrinth seal 27 provided at the peripheral edge of the movable substrate 49. Has been.

  A single drive hole 54 is provided at the center of the pedestal 52 as clearly shown in FIG. In the vicinity of the drive hole 54 in the pedestal portion 52, a pressure introduction path vertical portion 55 extending vertically upward is opened. The pressure introduction path vertical part 55 communicates with the pressure introduction port 22 via the pressure introduction path horizontal part 21.

  An eccentric shaft 56 is attached to the drive hole 54 of the pedestal 52. The structure of the upper end large diameter portion 30 of the eccentric shaft 56 is the same as that of the eccentric shaft 28 shown in FIG. 7, but the rotating shaft 57 is slightly different. A lower frame 58 is attached to the lower end of the support frame 50 and supports the lower portion of the rotary shaft 57 via a bearing 59. Although not shown, a known anti-rotation mechanism for preventing the floating scroll 48 from rotating is provided between the movable substrate 49 of the floating scroll 48 and the pedestal 52.

  According to this scroll compressor, when the rotating shaft 57 is driven by the motor (not shown) and the eccentric shaft 56 rotates, the engaging shaft 51 rotates in the eccentric recess 31 through the engagement with the orbiting bearing 39. It rotates around the axis of the shaft 57. Thereby, the floating scroll 2 performs a revolving motion in which the rotation is prevented, and the compression of the gas in the compression chamber 8 is performed based on the action of a known scroll compressor.

  The action of the pressure chamber 23 and the labyrinth seal 27 is the same as that of the first embodiment described with reference to FIGS. The effect is the same as that of the first embodiment except that a rotation prevention mechanism is necessary.

  In the scroll compressor of the present invention, the position of the orbiting scroll is stably and appropriately automatically adjusted with a simple configuration, and the sealing performance of the compression chamber is reliably maintained while avoiding contact between the scroll front end and the opposed surface. Therefore, the durability related to the wear of the scroll tip is improved, and it is useful as a compressor for air or refrigerant.

DESCRIPTION OF SYMBOLS 1 Fixed scroll 2, 48 Floating scroll 3, 50 Support frame 4 Fixed board | substrate 5 1st spiral blade 5a Cylindrical outer peripheral wall 6, 49 Movable board | substrate 7 2nd spiral blade 8 Compression chamber 9 Discharge path vertical part 10 Discharge path horizontal part 11 Discharge port 12 Suction passage vertical portion 13 Suction passage horizontal portion 14 Suction port 15, 52 Pedestal portion 16 Upper cylindrical portion 17 Lower cylindrical portion 18 Fitting inner peripheral surface 19, 54 Drive hole 20 Pressure introduction passage vertical portion 21 Pressure introduction passage horizontal Portion 22 Pressure inlet port 23, 53 Pressure chamber 24, 51 Engagement shaft 25 Projection wall 26 Labyrinth groove 27 Labyrinth seal 28, 56 Eccentric shaft 29, 57 Rotating shaft 30 Upper end large-diameter portion 31 Eccentric recess 31a Clearance 32 Bearing mounting portion 33 Large-diameter portion accommodating portion 34 Leap seal mounting portion 35 Shaft insertion hole 36 Large-diameter portion bearing 37 Leap seal 38 Bush 39 Turning Bearings 40 and 58 the lower frame 41,59 bearing 42 horizontal spindle bearing holder 43 driving shaft 44, 45 gear 46 direction gap 47 longitudinally gap

In order to solve the above problem, the scroll compressor of the present invention, the projection wall protruding toward the base portion is provided on the periphery of the lower surface of the movable substrate, the pressure by the enclosed recess by front Stories projection wall A chamber is formed, and a pressure introduction path for introducing a part of the gas compressed in the compression chamber into the pressure chamber is provided, and the interval between the fixed scroll and the pedestal portion is predetermined in the vertical direction of the floating scroll. is set movable as a range, the communicated with the pressure chamber outside the low pressure region of the projection wall through the gap formed between the tip surface of the projection wall and the base portion, the pressure chamber of the gas wherein a can be discharged to the low pressure region, wherein the front end surface of the projection wall labyrinth seal provided with a labyrinth groove extending in the circumferential direction is formed between the upper surface of the pedestal portion and the labyrinth seal Gas pressure in the pressure chamber, characterized in that it is adjusted in accordance with the.

Claims (4)

A fixed scroll having a configuration in which a first spiral blade is provided on the lower surface of the fixed substrate;
A floating scroll having a configuration in which a second spiral blade is provided on the upper surface of the movable substrate;
An eccentric drive element for revolving the floating scroll is disposed on a pedestal portion, and the floating scroll is interposed between the pedestal portion and the fixed scroll so as to be capable of revolving, and A combined support frame,
In the scroll compressor in which the first and second spiral blades are engaged with each other to form a compression chamber, and the compression chamber moves while reducing the volume by the revolution of the floating scroll, and the compression of the gas is performed.
Protruding walls projecting toward the pedestal portion are provided on the peripheral edge of the movable substrate, and a pressure chamber is formed by the projecting wall surrounding the gap between the movable substrate and the pedestal portion,
A pressure introduction path for introducing a part of the gas compressed in the compression chamber into the pressure chamber;
An interval between the fixed scroll and the pedestal portion is set so that the floating scroll is movable within a predetermined range in a vertical direction, and the pressure chamber is passed through a gap formed between a tip surface of the protruding wall and the pedestal portion. Can communicate with a low pressure region outside the protruding wall,
A scroll compressor characterized in that a labyrinth groove extending in the circumferential direction is provided on a tip surface of the protruding wall to form a labyrinth seal.   The front end surface of the first spiral blade and the upper surface of the movable substrate, and the front end surface of the second spiral blade and the lower surface of the fixed substrate directly face each other without interposing other elements. The scroll compressor described. An eccentric shaft that is rotatably mounted on the pedestal as the eccentric drive element and faces the lower surface of the movable substrate;
The upper end surface portion of the eccentric shaft is provided with a circular eccentric recess having a central axis at a position eccentric with respect to the rotational axis of the eccentric shaft,
An engagement shaft extending toward the pedestal portion is provided on the lower surface of the movable substrate, and the engagement shaft is mounted in the eccentric recess of the eccentric shaft,
The scroll compressor according to claim 1 or 2, wherein the floating scroll is driven to revolve through the engagement of the eccentric recess and the engagement shaft by the rotation of the eccentric shaft.   The scroll compressor according to claim 3, wherein a pair of the engagement shafts are provided and arranged on opposite sides with respect to the center axis of the revolution.

Images