JP2009052463A - Scroll compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To increase the reliability of a fixed scroll and a rotary scroll of a scroll compressor to match the compressor to recent refrigerating air conditioners increased in efficiency and life and using a high-pressure refrigerant such as carbon dioxide. <P>SOLUTION: A communication passage 80 allowing a high-pressure part 30 on the inside of a sliding partition ring 78 to communicate with a compression chamber 15 is formed in the rotary scroll 13. An opening 81 on the compression chamber 15 side of the communication passage 80 is so formed at the lap end 13b of the rotary scroll 13 as not to face discharge bypass ports 40 and a discharge port 18 at the center of the fixed scroll 12. Since the lap end 13b of the rotary scroll 13 is prevented from coming into nonuniform contact with the end plate 12a of the fixed scroll 12 when the scroll compressor is under high load, the high reliability of the scroll compressor can be realized. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a scroll compressor used in a cooling device such as a cooling / heating air conditioner or a refrigerator, or a heat pump type hot water supply device.

  2. Description of the Related Art Conventionally, scroll compressors used in refrigeration air conditioners and refrigerators generally form a compression chamber between the fixed scroll and the orbiting scroll in which the spiral wrap rises from the end plate, and the orbiting scroll is rotated by a rotation restraint mechanism. When it is swung along a circular orbit under the constraint of the above, suction, compression, and discharge are performed by moving the compression chamber while changing the volume. During operation, pressure is applied to the orbiting scroll from the back, and the orbiting scroll is stuck to the fixed scroll. Further, since the working fluid is compressed toward the center and becomes a high-temperature and high-pressure state, the orbiting scroll and the fixed scroll are also heated at the center, resulting in a dimensional change due to thermal expansion. In particular, this phenomenon appears remarkably under high-load operating conditions, and there is a risk that seizure will occur due to the contact between the top surface of the fixed scroll and the end plate of the orbiting scroll. Therefore, for the wrap portion of the orbiting scroll or fixed scroll, a tip seal is provided at the tip of the wrap portion, and oil is guided to the back of the tip seal to improve the seal performance of the tip seal, and from the tip seal to the compression chamber. The oil which leaks has taken the structure which has improved the lubricity of the sliding surface (for example, refer patent document 1).

FIG. 8 is a cross-sectional view of a conventional scroll compressor described in Patent Document 1. In FIG. As shown in FIG. 8, a tip seal groove 93 is provided in the wrap tip 13 b of the orbiting scroll 13 and the wrap tip 12 b of the fixed scroll 12, and a tip seal 92 is attached thereto. The orbiting scroll 13 is formed with a communication passage 80 that allows the tip seal groove 93 and the orbiting scroll back portion 30 to communicate with each other, and the oil 6 in the orbiting scroll 13 back portion 30 is supplied to the tip seal groove 93. As a result, the entire surface of the tip seal 92 is covered with the oil 6 to improve the sealing performance, and the tip seal 92 attached to the orbiting scroll 13 is pressed against the tooth bottom 12a of the fixed scroll 12 by the oil pressure. Leakage from the wrap tip 13b can be reduced. Further, the oil leaking from the tip seal 92 to the compression chamber improves the lubricity of the sliding surface.
JP-A-6-288361

  However, in the conventional configuration described in Patent Document 1, since the tip seal groove that communicates with the suction space opens from the discharge pressure space, the amount of oil supply according to the differential pressure between the discharge pressure and the suction pressure Is continuously supplied into the suction chamber. As a result, when the high differential pressure operation is performed, there is a problem in that the volumetric efficiency decreases due to the intake refrigerant being heated by a large amount of relatively high-temperature oil. . In addition, when the oil supplied to the suction chamber is compressed and compressed toward the center, the oil becomes high temperature and the viscosity becomes low. When the oil is supplied to the center of the compression chamber where sliding is relatively severe, As a result, the cooling effect is lost and the cooling effect is lost. In particular, the wrap tip of the fixed scroll and the end plate portion of the orbiting scroll may come into contact with each other.

In particular, when carbon dioxide is used as the refrigerant, the pressure difference between the discharge pressure of the compressor and the suction pressure is about 7 to 10 times higher than the pressure difference of the refrigeration cycle of the conventional HFC refrigerant. There is a problem that deformation becomes easier to the side, galling occurs at the end of the orbiting scroll and the tip of the lap portion, and the compressor efficiency and durability as a compressor are reduced.

  Accordingly, the present invention has been made in view of the above-described conventional problems, and by supplying an appropriate amount of oil stably to the central portion of the compression chamber that is in a high temperature and high differential pressure state, the wrap tip of the fixed scroll It is an object of the present invention to provide a scroll compressor that can prevent seizure of the head portion and the end plate portion of the orbiting scroll and ensure high reliability. Another object of the present invention is to realize a highly efficient scroll compressor by suppressing performance deterioration due to a decrease in volumetric efficiency due to suction heating.

  In order to solve the above-described conventional problems, the scroll compressor according to the present invention includes a discharge bypass port that bypasses the compression chamber and the high-pressure space in the fixed scroll, and a discharge port in the center, and the high-pressure portion and the compression chamber communicate with each other. The communication passage is provided in the inside of the orbiting scroll, and the opening on the compression chamber side of the communication passage is provided at the end of the orbiting scroll so as not to face the discharge bypass port and the discharge port.

  With this configuration, a high pressure is applied to the back of the orbiting scroll under a high load, the orbiting scroll is deformed to the fixed scroll side due to the differential pressure between the discharge pressure and the suction pressure, and the fixed scroll wrap becomes hot due to the compression heat. In particular, the center expands thermally toward the orbiting scroll. However, since oil is supplied to the compression chamber in the center, the cooling effect and lubricity can be improved to prevent contact and achieve high reliability. . Further, since oil is supplied to the compression chamber that is relatively close to the end of compression, oil is positively supplied to the compression chamber during high differential pressure operation that results in insufficient compression. And since the opening part of the wrap front-end | tip of a turning scroll is provided in the position which does not face a discharge port, an appropriate amount of oil can be supplied to a compression chamber.

  On the other hand, the opening at the wrap tip of the orbiting scroll is provided at a position that does not face the discharge bypass port, so there is no re-expansion due to the compressed gas entering the discharge bypass port, and suction due to oil supply to the suction chamber A highly efficient scroll compressor can be realized without heating.

  The scroll compressor according to the present invention can prevent seizure of the wrap tip of the fixed scroll and the end plate of the orbiting scroll by stably supplying an appropriate amount of oil to the compression chamber that is in a high temperature and high pressure state. A highly efficient scroll compressor can be realized by ensuring high reliability and suppressing suction heating and re-expansion.

  According to a first aspect of the present invention, a discharge bypass port that bypasses the compression chamber and the high-pressure space in the fixed scroll, a discharge port in the center, and a communication passage that connects the high-pressure portion and the compression chamber are provided inside the orbiting scroll. The opening on the compression chamber side of the passage is provided at the wrap tip of the orbiting scroll so as not to face the discharge bypass port and the discharge port. With this configuration, a high pressure is applied to the back of the orbiting scroll under a high load, the orbiting scroll is deformed to the fixed scroll side due to the differential pressure between the discharge pressure and the suction pressure, and the fixed scroll wrap becomes hot due to the compression heat. As a result, the center portion is thermally expanded toward the orbiting scroll. However, since oil is supplied to the compression chamber in the center portion, it is possible to prevent a single contact and realize high reliability. In addition, since the opening at the tip of the orbiting scroll wrap is provided at a position not facing the discharge port, an appropriate amount of oil can be supplied to the compression chamber.

On the other hand, the opening at the wrap tip of the orbiting scroll is provided at a position that does not face the discharge bypass port, so there is no re-expansion due to the compressed gas entering the discharge bypass port, and suction due to oil supply to the suction chamber A highly efficient scroll compressor can be realized without heating.

  The second invention is particularly the first invention, and the opening is located between the discharge port and the discharge bypass port. With this configuration, since the opening is between the discharge port and the discharge bypass port, oil is supplied to the compression chamber that is relatively close to the end of compression, and a large amount of oil is actively used during high differential pressure operation that results in insufficient compression. Therefore, high reliability can be realized without the wrap tip of the fixed scroll and the end plate of the orbiting scroll coming into contact with each other.

  The third invention is the second invention, in which the hole diameter of the opening is 5 to 50% of the wrap thickness of the orbiting scroll. According to this configuration, by setting the hole diameter of the opening to 5% or more of the wrap thickness of the orbiting scroll, it is possible to supply a sufficient amount of oil for lubrication and the wrap tip of the fixed scroll and the end plate of the orbiting scroll come into contact with each other. High reliability can be realized. Moreover, by setting the hole diameter of the opening to 50% or less of the wrap thickness of the orbiting scroll, leakage at the wrap tip of the orbiting scroll due to the provision of the opening can be suppressed, and a highly efficient scroll compressor can be provided. realizable.

  The fourth aspect of the invention is particularly the third aspect of the invention, wherein a part of the communication path is made into a fine hole having a throttle effect. In the case of a large compressor, since the thickness of the end plate is increased, it is difficult to penetrate through the pores for processing. Therefore, by forming a part of the communication path as a fine hole having a throttling effect, it is possible to process and to adjust the oil supply amount to an appropriate amount.

  The fifth aspect of the invention is the third or fourth aspect of the invention, in which a groove is formed on the upper surface of the wrap of the orbiting scroll and opens to the opening of the communication path. As a result, oil can be supplied to a wide area of the compression chamber, so that higher reliability can be realized without the wrap tip of the fixed scroll and the end plate of the orbiting scroll coming into contact with each other.

  The sixth invention is particularly the fifth invention, wherein the groove width is not less than the hole diameter of the opening and not more than 80% of the wrap thickness of the orbiting scroll. According to this structure, the burr | flash which generate | occur | produces when processing the hole of an opening part can be reliably removed by making the groove width of a groove | channel more than the hole diameter of an opening part. In addition, by setting the groove width to 80% or less of the wrap thickness of the orbiting scroll, leakage at the wrap tip of the orbiting scroll due to the provision of the groove can be suppressed, and a highly efficient scroll compressor is realized. it can.

  The seventh invention is the sixth invention, in which the groove depth is 0.1 to 2% of the wrap height of the orbiting scroll. According to this configuration, by setting the depth of the groove to 0.1% or more of the wrap height of the orbiting scroll, the oil is filled in the entire area of the groove, so that the oil can be reliably supplied over a wide area of the compression chamber. Therefore, higher reliability can be realized without causing the wrap tip of the fixed scroll and the end plate of the orbiting scroll to come into contact with each other. Further, by setting the depth of the groove to 2% or less of the wrap height of the orbiting scroll, it is possible to reliably supply an appropriate amount of oil to the wide area of the compression chamber by the squeezing effect in the groove portion.

  The eighth invention is any one of the first to seventh inventions, and uses carbon dioxide as the working refrigerant.

Since the carbon dioxide refrigerant is a high differential pressure refrigerant, an excessive pressing force is generated on the surface on which the end plate of the orbiting scroll and the end plate of the fixed scroll slide. It will cause abnormal wear. In particular, the orbiting scroll is more easily deformed to the fixed scroll side, causing galling at the bottom of the end plate of the orbiting scroll and the tip of the wrap portion of the fixed scroll, reducing the compressor efficiency and durability as a compressor. End up. When carbon dioxide refrigerant is used, the pressure difference between the discharge pressure and the suction pressure of the compressor is about 7 to 10 times higher than the pressure difference of the conventional refrigeration cycle using chlorofluorocarbon as a refrigerant. Furthermore, the performance was reduced. According to the first to seventh aspects of the invention, even when there is a pressure deformation of the orbiting scroll due to a differential pressure between the discharge pressure and the suction pressure at high load, high reliability can be realized without hitting. Further, high efficiency can be realized in the entire operation region.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

(Embodiment 1)
1 is a longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention, FIG. 2 is an enlarged sectional view of a main part of the compression mechanism section of FIG. 1, and FIG. 3 is a view of the compression mechanism section of FIG. It is a top view. The operation and action of the scroll compressor configured as shown in the figure will be described below.

  As shown in FIG. 1, the scroll compressor of the present invention includes a main bearing member 11 of a crankshaft 4 fixed by welding or shrink fitting in an airtight container 1, and a fixed bolted on the main bearing member 11. The scroll-type compression mechanism 2 is configured by sandwiching the orbiting scroll 13 that meshes with the fixed scroll 12 between the scroll 12 and prevents the orbiting scroll 13 from rotating between the orbiting scroll 13 and the main bearing member 11. A rotation restricting mechanism 14 such as an Oldham ring that guides the orbital motion is provided, and the orbiting scroll 13 is eccentrically driven by the eccentric shaft portion 4 a at the upper end of the crankshaft 4, thereby causing the orbiting scroll 13 to move circularly. Thus, the compression chamber 15 formed between the fixed scroll 12 and the orbiting scroll 13 is small while moving from the outer peripheral side to the center portion. The refrigerant gas is sucked and compressed from the suction pipe 16 communicating with the outside of the hermetic container 1 and the suction port 17 on the outer peripheral portion of the fixed scroll 12, and the refrigerant gas exceeding the predetermined pressure is fixed. The reed valve 19 is pushed open from the discharge port 18 at the center of the scroll 12 and discharged into the sealed container 1 repeatedly.

  A sliding partition ring 78 disposed on the main bearing member 11 is provided on the back surface portion of the orbiting scroll 13, and the high pressure portion that is an inner region of the sliding partition ring 78 is formed by the sliding partition ring 78 while performing the orbiting motion. 30 and a back pressure space 29 set to an intermediate pressure of high pressure and low pressure, which is an outer region. By applying pressure on the back surface, the orbiting scroll 13 is stably pressed against the fixed scroll 12, reducing leakage and performing stable circular orbit movement.

  Further, the fixed scroll 12 includes a back pressure adjusting valve 9 that controls the pressure in the back pressure space 29 on the back surface of the orbiting scroll 13.

  During operation of the compressor, a pump 25 is provided at the other downward end of the crankshaft 4 and is driven simultaneously with the scroll compressor. As a result, the pump 25 sucks up the oil 6 in the oil reservoir 20 provided at the bottom of the hermetic container 1 and supplies it to the compression mechanism 2 through the oil supply hole 26 extending vertically through the crankshaft 4. The supply pressure at this time is substantially equal to the discharge pressure of the scroll compressor, and also serves as a back pressure source for the orbiting scroll 13. As a result, the orbiting scroll 13 does not move away from the fixed scroll 12 and does not come into contact with each other, and the predetermined compression function is stably exhibited.

  A part of the oil 6 supplied in this way is obtained by a supply pressure or its own weight so as to obtain a clearance, between the fitting portion between the eccentric shaft portion 4a and the orbiting scroll 13, and between the crankshaft 4 and the main bearing member 11. Then, the oil enters the bearing portion 66, lubricates the respective portions, falls, and returns to the oil sump 20.

Further, the oil 6 supplied to the high pressure section 30 is communicated with the communication path 5 provided inside the orbiting scroll.
4 enters the back pressure space 29 around the outer peripheral portion of the orbiting scroll 13 where the rotation restricting mechanism 14 is located, and the sliding portion by the meshing of the fixed scroll 12 and the orbiting scroll 13 and the sliding of the rotation restricting mechanism 14. Along with lubricating the moving part, the back pressure of the orbiting scroll 13 is applied in the back pressure space 29.

  The oil 6 entering the back pressure space 29 is set to an intermediate pressure that is intermediate between the pressures of the high pressure portion 30 and the low pressure side of the compression chamber 15 by the throttle action of the throttle 57. The back pressure space 29 is sealed between the high pressure portion 30 and the high pressure side by an annular partition ring 78. The pressure increases as the incoming oil is filled, and when the pressure exceeds a predetermined pressure, the back pressure adjusting valve 9 Acts to return to the suction portion of the compression chamber 15 and enter.

  The approach of the oil 6 is repeated at a predetermined cycle, and the timing of this repetition depends on the combination of the repetitive cycle of suction, compression, and discharge and the relationship between the pressure setting by the throttle hole 57 and the pressure setting by the back pressure adjusting mechanism 9. As a result, the sliding of the fixed scroll 12 and the wrap 13b of the orbiting scroll 13 is intentionally lubricated. This intentional lubrication is always ensured by the opening of the communication path 10 into the recess 105 by the back pressure regulating valve 9 as described above. The oil 6 supplied to the suction port 17 moves to the compression chamber 15 along with the orbiting motion of the orbiting scroll 13 and serves to prevent leakage between the compression chambers 15.

  Further, as shown in FIGS. 1 to 3, the fixed scroll 12 is provided with a discharge bypass port 40 that bypasses the compression chamber 15, the discharge muffler 77, and the high-pressure space 31 sandwiched between the fixed scroll 13. As a result, when the compression chamber 15 reaches a certain pressure or higher, the compressed gas can be released from the discharge bypass port to the high-pressure space 31, thereby preventing over-compression in the compression chamber 15.

  Further, a communication passage 80 that communicates the high-pressure portion 30 that is the inner region of the sliding partition ring 78 and the compression chamber 15 is provided inside the orbiting scroll 13, and an opening 81 on the compression chamber 15 side of the communication passage 80 is provided in the discharge bypass. This is provided at the wrap tip 13 b of the orbiting scroll 13 so as not to face the port 40 and the discharge port 18 at the center of the fixed scroll 12.

  With this configuration, a high pressure is applied to the back surface of the end plate 13a of the orbiting scroll 13 at a high load, and the orbiting scroll 13 is deformed to the fixed scroll 12 side by the differential pressure between the discharge pressure and the suction pressure, and the fixed scroll 12 is wrapped. The thermal expansion of 12b to the orbiting scroll 13 side is caused by the high temperature due to the compression heat. However, the oil 6 of the high pressure portion 30 that is the inner region of the sliding partition ring 78 is provided inside the orbiting scroll 13. Since the oil is supplied to the compression chamber 15 through the communication path 80, the oil 6 can be prevented from being hit by the cooling effect and lubricity, and high reliability can be realized. In addition, since the opening 81 of the wrap tip 13 b of the orbiting scroll 13 is provided at a position not facing the discharge port 18, an appropriate amount of oil 6 can be supplied to the compression chamber 15.

  On the other hand, since the opening 81 of the wrap tip 13b of the orbiting scroll 13 is provided at a position that does not face the discharge bypass port 40, there is no re-expansion due to the compressed gas entering the discharge bypass port 40. A high-efficiency scroll compressor can be realized without suction heating due to the oil supply to the suction chamber.

  The opening 81 is located between the discharge port 18 and the discharge bypass port 40.

With this configuration, since the opening 81 is between the discharge port 18 and the discharge bypass port 40, oil is supplied to the compression chamber 15 that is relatively close to the end of compression, and a large amount of pressure is required during high differential pressure operation that results in insufficient compression. The oil 6 is positively supplied to the compression chamber 15, and high reliability can be realized without the wrap tip 12 b of the fixed scroll 12 and the end plate 13 a of the orbiting scroll 13 coming into contact with each other.

(Embodiment 2)
In the scroll compressor according to the second embodiment of the present invention, the hole diameter 81d of the opening 81 is 5 to 50% of the wrap thickness 12t of the orbiting scroll 13. FIG. 4 is a cross-sectional view of the orbiting scroll according to Embodiment 2 of the present invention.

  If the amount of oil supplied from the high pressure section 30 to the compression chamber 15 is too small, abnormal sliding or seizure may occur. On the other hand, the greater the amount of oil, the better the lubrication and the better the sliding state of the wrap tip 12b of the fixed scroll 12 and the end plate 13a of the orbiting scroll 13 will be. However, since the inside of the compression chamber 15 becomes oil rich, a large amount of oil inevitably intervenes between the laps of both scrolls, which causes an increase in viscosity loss.

  Therefore, according to this configuration, by setting the hole diameter of the opening 81 to 5% or more of the wrap thickness 13t of the orbiting scroll 13, an oil amount 6 sufficient for lubrication can be supplied to the compression chamber 15, and the wrap of the fixed scroll 12 can be supplied. High reliability can be realized without the tip 12b and the end plate 13a of the orbiting scroll 13 coming into contact with each other. In addition, by setting the hole diameter of the opening 81 to 50% or less of the wrap thickness 13t of the orbiting scroll 13, leakage at the wrap tip 13b of the orbiting scroll 13 due to the provision of the opening 81 can be suppressed. An efficient scroll compressor can be realized.

(Embodiment 3)
In the scroll compressor according to the third embodiment of the present invention, a part of the communication path 80 is made into a fine hole having a throttling effect. FIG. 5 is a cross-sectional view of the orbiting scroll according to Embodiment 3 of the present invention.

  In the case of a large compressor, since the thickness of the end plate 13a of the orbiting scroll 13 is increased, it is difficult to penetrate the communication passage 80 through the pores for processing. Therefore, by forming a part of the communication path 80 as a fine hole having a throttling effect, it is possible to process and adjust the oil supply amount to an appropriate amount.

(Embodiment 4)
In the scroll compressor according to the fourth embodiment of the present invention, a groove 82 is formed on the upper surface of the wrap 13 b of the orbiting scroll 13 and opens to the opening 81 of the communication path 80. 6 is a plan view of a compression mechanism section according to Embodiment 4 of the present invention, and FIG. 7 is a cross-sectional view of the compression mechanism section.

  As a result, the oil 6 can be supplied over a wide area of the compression chamber 15, so that higher reliability can be realized without the wrap tip 12 b of the fixed scroll 12 and the end plate 13 a of the orbiting scroll 13 coming into contact with each other.

  Further, as shown in FIG. 6, the groove width 82 w of the groove 82 is not less than the hole diameter 81 d of the opening 81 and not more than 80% of the wrap thickness 13 t of the orbiting scroll 13.

  According to this configuration, by setting the groove width 82w of the groove 82 to be equal to or larger than the hole diameter 81d of the opening 81, burrs generated when the hole of the opening 81 is processed can be reliably removed. Further, by setting the groove width 32w of the groove 32 to 80% or less of the wrap thickness 13t of the orbiting scroll 13, leakage at the wrap tip 13b of the orbiting scroll 13 due to the provision of the groove 82 can be suppressed. An efficient scroll compressor can be realized.

  Further, the depth 82h of the groove 82 is set to 0.1 to 2% of the wrap height of the orbiting scroll.

  According to this configuration, by setting the depth 82h of the groove 82 to 0.1% or more of the lap height 13t of the orbiting scroll 13, the entire region of the groove 82 is filled with the oil 6, so that the compression chamber Since the oil 6 can be reliably supplied to the wide area of 15, the wrap tip 12b of the fixed scroll 12 and the end plate 13a of the orbiting scroll 13 do not come into contact with each other, and higher reliability can be realized. Further, by setting the depth 82h of the groove 82 to 2% or less of the lap height 13h of the orbiting scroll 13, the oil 6 can be reliably supplied to the wide area of the compression chamber 15 by the squeezing effect in the groove 82 portion. Can be supplied.

(Embodiment 5)
The scroll compressor according to the fifth embodiment of the present invention uses carbon dioxide as a working refrigerant. Since the carbon dioxide refrigerant is a high differential pressure refrigerant, an excessive pressing force is generated on the surface on which the end plate of the orbiting scroll and the end plate of the fixed scroll slide. It will cause abnormal wear. In particular, the orbiting scroll is more easily deformed to the fixed scroll side, causing galling at the bottom of the end plate of the orbiting scroll and the tip of the wrap portion of the fixed scroll, reducing the compressor efficiency and durability as a compressor. End up. When carbon dioxide refrigerant is used, the pressure difference between the discharge pressure and the suction pressure of the compressor is about 7 to 10 times higher than the pressure difference of the conventional refrigeration cycle using chlorofluorocarbon as a refrigerant. Furthermore, the performance was reduced. According to the first to fourth embodiments, even when there is pressure deformation of the orbiting scroll due to the differential pressure between the discharge pressure and the suction pressure at high load, high reliability can be realized without hitting. Further, high efficiency can be realized in the entire operation region.

  As described above, the scroll compressor according to the present invention can achieve high reliability even under high differential pressure operation, and the air scroll compressor, the vacuum pump, the scroll type expansion can be realized without limiting the working fluid to the refrigerant. It can also be applied to the use of scroll fluid machines such as machines.

The longitudinal cross-sectional view of the scroll compressor in Embodiment 1 of this invention Sectional drawing of the compression mechanism part of the scroll compressor in Embodiment 1 of this invention The top view of the compression mechanism part of the scroll compressor in Embodiment 1 of this invention Sectional drawing of the turning scroll of the scroll compressor in Embodiment 2 of this invention Sectional drawing of the turning scroll of the scroll compressor in Embodiment 3 of this invention The top view of the compression mechanism part of the scroll compressor in Embodiment 4 of this invention Sectional drawing of the compression mechanism part of the scroll compressor in Embodiment 4 of this invention Sectional view of a conventional scroll compressor

Explanation of symbols

6 Oil 11 Main bearing member 12 Fixed scroll 12a End plate 12b Wrap 13 Orbiting scroll 13a End plate 13b Wrap 13t Wrap thickness 13h End plate thickness 14 Rotation restricting mechanism 15 Compression chamber 17 Suction port 18 Discharge port 29 Back pressure space 30 High pressure portion 31 High pressure space 40 Discharge bypass port 77 Discharge muffler 78 Sliding partition ring 80 Communication path 81 Opening 82 Groove 82w Groove width 82h Groove depth

Claims (8)

By meshing the fixed scroll and the orbiting scroll where the spiral wrap rises from the end plate, and moving the orbiting scroll along a circular orbit under the regulation of rotation, the volume is changed, so that suction, compression, A compression chamber for discharging is formed, and a ring-shaped groove is provided in a bearing member that substantially supports the orbiting scroll and the back side of the end plate, and a high pressure is applied to the bearing member and the central part on the back side of the end plate by lubricating oil. The high pressure portion to be applied and the high pressure portion are partitioned by a ring-shaped sliding partition ring having a joint portion attached to the groove portion, and a predetermined pressure lower than that of the high pressure portion is applied to the outer peripheral portion of the rear surface of the orbiting scroll end plate In a scroll compressor provided with a back pressure space to
A discharge bypass port that bypasses the compression chamber and the high-pressure space in the fixed scroll, a discharge port in the center, and a communication passage that communicates the high-pressure portion and the compression chamber are provided in the orbiting scroll, and the communication A scroll compressor characterized in that an opening of the passage on the side of the compression chamber is provided at a wrap end of the orbiting scroll so as not to face the discharge bypass port and the discharge port. The scroll compressor according to claim 1, wherein the opening is located between the discharge port and the discharge bypass port. The scroll compressor according to claim 2, wherein a hole diameter of the opening is set to 5 to 50% of a wrap thickness of the orbiting scroll. The scroll compressor according to claim 3, wherein a part of the communication path is a fine hole having a throttling effect. The scroll compressor according to claim 3 or 4, wherein a groove is formed on the upper surface of the wrap of the orbiting scroll, and the opening is formed in the opening of the communication path. The scroll compressor according to claim 5, wherein a groove width of the groove is not less than a hole diameter of the opening and not more than 80% of a wrap thickness of the orbiting scroll. The scroll compressor according to claim 5 or 6, wherein a depth of the groove is 0.1 to 2% of a wrap height of the orbiting scroll. The scroll compressor according to any one of claims 1 to 7, wherein carbon dioxide is used as a working refrigerant.

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