JP2010168910A - Scroll compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a scroll compressor in which compressor efficiency is improved by suppressing in a simple constitution the increase in leakage loss and slide loss at a scroll lap tip under a plurality of pressure conditions requiring year-round performance. <P>SOLUTION: A scroll compressor includes an intermediate pressure chamber 23 for imparting a pressing force to a turning scroll, a fluid inflow means for forcing fluid to flow into the intermediate pressure chamber 23 and a fluid outflow means 30 for forcing fluid in the intermediate pressure chamber 23 to flow out to a suction chamber or compression chamber. The fluid outflow means 30 includes a fluid flow-out path 27 and an intermediate pressure control valve 8. The intermediate pressure control valve 8 controls the pressure in the intermediate pressure chamber 23 to a first pressure suitable for the low pressure state under a low pressure state and to a second pressure suitable for the high pressure state under a high pressure state by changing a throttling amount to a fluid flowing through the fluid flow-out path 27 in response to a change of the pressure state. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a scroll compressor, and is particularly suitable for a scroll compressor having an intermediate pressure chamber that applies a pressing force to a fixed scroll to a turning scroll.

  Some scroll compressors have an intermediate pressure chamber formed on the back surface of the orbiting scroll so as to press the orbiting scroll against the fixed scroll in order to reduce leakage loss at the end of the scroll wrap. If the pressure in the intermediate pressure chamber is too high, the sliding loss at the tip of the scroll wrap increases and the compressor efficiency decreases, so it is necessary to adjust to an appropriate pressure.

  Japanese Patent Laid-Open No. 10-110688 (Patent Document 1) discloses a scroll compressor having means for adjusting the force for pressing the orbiting scroll against the fixed scroll. In the scroll compressor of Patent Document 1, a differential pressure control valve is provided between the intermediate pressure chamber and the suction chamber in order to adjust the force for pressing the orbiting scroll against the fixed scroll, and the intermediate pressure is set to a constant value for the suction pressure. By controlling the applied pressure, the refrigerant gas is discharged from the compression chamber by the bypass valve when the pressure in the compression chamber becomes larger than the discharge pressure.

JP-A-10-110688

  In recent years, the annual energy consumption efficiency indicated by the performance of room air conditioners and the annual hot water supply efficiency indicated by the performance of heat pump water heaters are expressed throughout the year. There are several. However, in the scroll compressor of each embodiment of Patent Document 1, the intermediate pressure is set under any one of a plurality of pressure conditions that require performance, and when operating under other pressure conditions. However, there was a problem that the performance deteriorated. That is, if an appropriate intermediate pressure is set for the low pressure condition, when the scroll compressor is operated under the high pressure condition, the sliding loss at the tip of the scroll wrap increases, and the compressor efficiency decreases. On the other hand, when an appropriate intermediate pressure is set for the high pressure condition, when the scroll compressor is operated under the low pressure condition, the leakage loss at the scroll wrap tip increases and the compressor efficiency decreases.

  An object of the present invention is to obtain a scroll compressor that can suppress the increase in leakage loss and sliding loss at a scroll wrap tip under a plurality of pressure conditions that require performance throughout the year with a simple configuration, and can improve compressor efficiency. There is.

  In order to achieve the above-mentioned object, the present invention has a fixed scroll having a base plate and a scroll wrap standing on the base plate, a base plate and a scroll wrap standing on the base plate, An orbiting scroll that forms a suction chamber or a compression chamber with the fixed scroll by engaging with the fixed scroll and performing an orbiting motion, an intermediate pressure chamber that applies a pressing force to the orbiting scroll toward the fixed scroll, and the intermediate Fluid inflow means for injecting fluid into the pressure chamber; and fluid outflow means for outflowing fluid in the intermediate pressure chamber to the suction chamber or compression chamber, wherein the fluid outflow means includes the intermediate pressure chamber and the suction chamber. Or a scroll compressor comprising a fluid outflow passage connecting the compression chamber and an intermediate pressure control valve provided in the fluid outflow passage for adjusting the pressure of the intermediate pressure chamber. The intermediate pressure control valve changes a throttle amount with respect to the fluid flowing through the fluid outflow passage in accordance with a change in the pressure state, and the first pressure suitable for the low pressure state is set in the low pressure state. In the high pressure state, the pressure in the intermediate pressure chamber is controlled to a second pressure suitable for the high pressure state.

A more preferable specific configuration example of the present invention is as follows.
(1) The intermediate pressure control valve is movably disposed in the fluid outflow passage and is in contact with a valve seat surface provided in the fluid outflow passage, and the valve seat is attached to the valve seat. An elastic body that applies a pressing force to the surface side, and the valve body forms a valve communication path that sets a throttle amount of the first pressure in a state in contact with the valve seat surface.
(2) The valve communication passage is provided on the valve seat surface side of the valve body, and is configured by a groove that communicates the inside and the outside of the valve seat surface.
(3) The groove constituting the valve communication path is a linear groove extending in the radial direction from the center of the valve body.
(4) The intermediate pressure control valve is movably disposed in the fluid outflow passage and is in contact with a valve seat surface provided in the fluid outflow passage, and the valve seat is connected to the valve seat. An elastic body that applies a pressing force to the surface side, and the valve seat surface forms a valve communication path that sets a throttle amount of the first pressure.
(5) To be used for heat pump water heaters, room air conditioners or refrigeration / refrigeration equipment.

  According to the scroll compressor of the present invention, it is possible to suppress an increase in leakage loss and sliding loss at the end of the scroll wrap under a plurality of pressure conditions that require performance throughout the year, and to improve the compressor efficiency, with a simple configuration. .

  Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. The same reference numerals in the drawings of the respective embodiments indicate the same or equivalent.

(First embodiment)
A scroll compressor according to a first embodiment of the present invention will be described with reference to FIGS.

  First, the whole scroll compressor 50 of this embodiment is demonstrated, referring FIGS. 1-3. FIG. 1 is a longitudinal sectional view of a scroll compressor 50 of the present embodiment, FIG. 2 is a view of the fixed scroll 2 of FIG. 1 as viewed from the side opposite to the scroll wrap, and FIG. 3 is a view of the fixed scroll 2 of FIG. It is the figure seen from the side. The scroll compressor 50 of the present embodiment is used as a component of a refrigeration cycle of a carbon dioxide-compatible heat pump hot water heater.

  The orbiting scroll 1 includes a base plate 1a, a scroll wrap 1b erected on the mirror surface of the base plate 1a, and a bearing holding portion 1d provided protruding from the back surface of the base plate 1a. . A turning Oldham groove 1e extending in the radial direction is formed on the back surface of the base plate 1a. The bearing holding portion 1d protrudes in a cylindrical shape. A cylindrical slewing bearing 1c is inserted into the bearing holding portion 1d.

  The fixed scroll 2 includes a substantially disk-shaped base plate 2n and a scroll wrap 2o provided upright on the mirror surface of the base plate 2n. The orbiting scroll 1 and the fixed scroll 2 are arranged to mesh with each other, and the suction chamber 16 and the compression chamber 3 are formed between the orbiting scroll 1 and the fixed scroll 2. As the orbiting scroll 1 revolves, the refrigerant gas is sucked through the suction chamber 16, compressed in the compression chamber 3, and discharged from the discharge hole 2 d of the fixed scroll 2 into the sealed container 22. The orbiting scroll 1 and the fixed scroll 2 constitute a compression mechanism unit.

  A non-turning reference surface 2a, which is the same surface as the tooth tip surface of the scroll wrap 2o, is provided on the peripheral edge of the base plate 2n of the fixed scroll 2 over the entire circumference. A peripheral groove 2b is formed in an annular shape on the non-turning reference surface 2a.

  Further, a fluid outflow means 30 including a fluid outflow path 27 and a back pressure control valve 8 is provided at the peripheral edge of the base plate 2 n of the fixed scroll 2. Details of the fluid outflow means 30 will be described later.

  Near the center of the fixed scroll 2, there is provided a discharge hole 2 d that is opened in the tooth bottom surface and discharges the working fluid compressed in the compression chamber 3.

  The tooth bottom of the fixed scroll 2 is provided with a total of four bypass holes 2c in two pairs. The reason for providing this bypass hole 2c is to extract the refrigerant gas from this bypass hole 2c so that the pressure in the compression chamber 3 does not become a predetermined discharge pressure or higher. A bypass valve plate 4 which is a reed valve plate is provided so as to cover and open the bypass hole 2c, and a retainer 4a is provided to limit the opening degree of the bypass valve plate 4. The bypass valve plate 4 and the retainer 4 a are fixed to the fixed scroll 2 by a common bypass screw 5.

  A suction dig 2e is provided at the outer edge of the tooth bottom surface of the fixed scroll 2, and a suction hole 2f is provided in communication with one side end of the suction dig 2e. The suction hole 2f extends from the back surface of the fixed scroll 2 so as to communicate with the suction dig 2e. A valve body 7a and a valve spring 7b are inserted into the suction hole 2f, and a suction pipe 6 is further inserted. The valve body 7a and the valve spring 7b constitute a check valve 7 on the suction side.

  A plurality of flow grooves 2 g are provided on the outer peripheral surface of the fixed scroll 2. The plurality of flow grooves 2g constitute a flow path serving as a flow path for the discharge gas and the lubricating oil 19 between the closed container 22 and are provided at intervals in the circumferential direction of the fixed scroll 2. It is provided at least near the outer peripheral surface upper end and near the outer peripheral surface lower end.

  A frame 9 is installed on the motor side of the fixed scroll 2. The frame 9 has the same outer diameter as the inner diameter of the sealed container 22 and is fixed to the sealed container 22 by welding.

  A plurality of flow grooves 9 h are provided on the outer peripheral surface of the frame 9. The plurality of flow grooves 9 h constitute a flow path serving as a flow path for the discharge gas and the lubricating oil 19 between the closed container 22 and communicate with the flow grooves 2 g of the fixed scroll 2. Are provided at intervals in the circumferential direction of the frame 9 and at least near the upper end of the outer peripheral surface and near the lower end of the outer peripheral surface.

  A surface on the fixed scroll side of the outer edge portion of the frame 9 is configured as an attachment surface 9 a to which the fixed scroll 2 is attached. The outer edge portion of the fixed scroll 2 and the mounting surface 9a of the frame 9 are brought into close contact with each other, and both 2 and 9 are fixed by a fixing screw 26.

  On the inner side (center side) of the mounting surface 9a of the frame 9, there is provided a swivel holding surface 9b that is a concave surface. The orbiting scroll 1 is sandwiched between the non-orbiting reference surface 2a of the fixed scroll 2 and the orbiting clamping surface 9b of the frame 9 so as to be orbitable.

  An Oldham ring installation surface 9 i that is a concave surface is provided on the inner side (center side) of the turning clamping surface 9 b of the frame 9. The Oldham ring installation surface 9i is provided with a frame-side Oldham groove 9c extending in the radial direction.

  A through-hole penetrating in the axial direction is provided in the center portion (center portion) of the frame 9. In this through hole, a shaft seal 9d and a main bearing 9e are installed in order from the motor side. A thrust surface 9f that receives the thrust force of the shaft 11 is provided at the scroll-side edge that forms the through hole. The thrust surface 9f is formed as a concave surface inside the Oldham ring installation surface 9i.

  The Oldham ring 10 has a frame-side protrusion 10a on one surface and a turning-side protrusion 10b on the other surface. The Oldham ring 10 is disposed between the Oldham ring installation surface 9i of the frame 9 and the back surface of the orbiting scroll 1, and the frame side protrusion 10a is movably fitted in the frame side Oldham groove 9c. 10b is movably fitted in the swivel Oldham groove 1e.

  An intermediate pressure chamber 23 that is a space surrounded by the orbiting scroll 1, the fixed scroll 2, and the frame 9 is formed on the back side of the orbiting scroll 1. The intermediate pressure chamber 23 is an intermediate pressure between the suction pressure and the discharge pressure, and constitutes a pressing force applying unit that applies a pressing force to the orbiting scroll 1 to the fixed scroll.

  The shaft 11 has a shaft oil supply hole 11a extending through the center portion to the bottom of the bearing holding portion 1d, a main bearing oil supply hole 11b extending in a radial direction from the shaft oil supply hole 11a to the main bearing 9e, and a shaft. A shaft seal oil supply hole 11c extending in the radial direction from the oil supply hole 11a and reaching the shaft seal 9d, and a sub bearing oil supply hole 11d extending in the radial direction from the shaft oil supply hole 11a and reaching the auxiliary bearing 13 are provided.

  An eccentric portion 11 e is provided at one end portion of the shaft 11. The eccentric portion 11e is inserted into the swivel bearing 1c. A narrow diameter portion 11 f is provided at the other end of the shaft 11. The small diameter portion 11f is inserted into the auxiliary bearing 13 and pivotally supported. The auxiliary bearing 13 has a spherical outer periphery and a cylindrical inner periphery. The auxiliary bearing 13 is incorporated in the auxiliary shaft housing 15, and the auxiliary shaft housing 15 is fixed to the auxiliary bearing support plate 14 fixed to the hermetic container 22.

  A rotor 12a is press-fitted and fixed to the central portion of the shaft 11. A stator 12b is shrink-fitted and fixed to the sealed container 22. The motor 12 includes a rotor 12a and a stator 12b.

  Next, the basic operation of the scroll compressor 50 having such a configuration will be described.

  As the rotor 12a rotates, the shaft 11 rotates, and the orbiting scroll 1 orbits due to the eccentric rotation of the eccentric portion 11e of the shaft 11. Here, since the Oldham ring 10 is provided, the rotation of the orbiting scroll 1 is prevented.

  Due to the orbiting motion of the orbiting scroll 1, the refrigerant gas of the refrigeration cycle is sucked into the suction chamber 16 through the suction pipe 6, and further enters the compression chamber 3 formed between the scrolls 1 and 2, and is compressed and discharged. The fixed scroll back chamber 17 is discharged from the hole 2d.

  The refrigerant gas discharged to the fixed scroll back chamber 17 collides with the sealed container 22 and the fixed scroll 2 to separate the lubricating oil, and passes through the flow grooves 2g and 9h provided on the outer peripheral surfaces of the fixed scroll 2 and the frame 9. Into the motor chamber 18. The lubricating oil separated in the fixed scroll back chamber 17 flows down into the lubricating oil 19 stored in the lower part of the fixed scroll back chamber 17.

  The refrigerant gas that has entered the motor chamber 18 collides with the rotor 12a, the stator 12b, the auxiliary bearing support plate 14 and the like to separate the lubricating oil contained in the refrigerant gas, and a vent hole formed in the auxiliary bearing support plate 14. 14a enters the oil storage chamber 21. The lubricating oil separated in the motor chamber 18 flows down into the lubricating oil 19 stored in the lower part of the motor chamber 18.

  The refrigerant gas entering the oil storage chamber 21 collides with the oil separation plate 25 to separate the lubricating oil contained in the refrigerant gas, and flows out through the discharge pipe 20. Note that the lubricating oil separated in the oil storage chamber 21 flows down into the lubricating oil 21 stored in the lower portion of the oil storage chamber 21.

  The pressure in the oil storage chamber 21 is slightly lower than the pressure in the motor chamber 18 due to the flow resistance of the refrigerant gas passing through the vent hole 14a. As a result, the lubricating oil 19 at the bottom of the motor chamber 18 is pushed out to the oil storage chamber 21 through the oil guide hole 14 b of the auxiliary bearing support plate 14 by the pressure of the motor chamber 18, and the oil in the oil storage chamber 21 from the oil level of the motor chamber 18. The surface becomes higher.

  The fixed scroll back chamber 17, the motor chamber 18, and the oil storage chamber 21 basically have an atmosphere of discharge pressure, although there is a slight pressure drop in this order due to the flow path resistance.

  Next, refueling in the scroll compressor 50 having such a configuration will be described.

  The lubricating oil 19 in the oil storage chamber 21 is a slewing bearing from the oil supply pipe 24 through the shaft oil supply hole 11a due to the differential pressure between the pressure in the oil storage chamber 21 (discharge pressure) and the pressure in the intermediate pressure chamber 23 (intermediate pressure). 1c is refueled. The lubricating oil 19 supplied to the slewing bearing 1c lubricates the sliding portion of the slewing bearing 1c, and after being depressurized, flows into the intermediate pressure chamber 23. As described above, the fluid inflow means for allowing the lubricating oil 19, which is a fluid, to flow into the intermediate pressure chamber 23, is constituted by oil supply means using differential pressure.

  A portion of the lubricating oil 19 that has flowed into the intermediate pressure chamber 23 flows out into the suction chamber 16 through the fluid outflow means 30, passes through the compression chamber 3 together with the refrigerant gas, and enters the fixed scroll back chamber 17 from the discharge hole 2 d of the fixed scroll 2. Discharged.

  Therefore, the intermediate pressure in the intermediate pressure chamber 23 is a pressure based on the differential pressure between the discharge pressure and the suction pressure, the throttle amount (channel resistance) in the slewing bearing 1c, and the throttle amount (channel resistance) in the fluid outflow means 30. Become.

  The lubricating oil passing through the shaft oil supply hole 11a passes through the main bearing oil supply hole 11b, the shaft seal oil supply hole 11c, and the auxiliary bearing oil supply hole 11d due to the centrifugal force generated by the rotation of the shaft 11, and the main bearing 9e, the shaft seal 9d, and the sub oil supply hole. Oil is also supplied to each sliding portion of the bearing 13.

  Next, the fluid outflow means 30 will be specifically described with reference to FIGS. 4 and 5. 4 is a cross-sectional view of the vicinity of the fluid outflow means 30 of FIG. 1, and FIG. 5 is a graph of intermediate pressure and operating pressure conditions when the scroll compressor 50 of FIG. 1 is used in a carbon dioxide-compatible heat pump hot water heater.

  First, it demonstrates using FIG. The fluid outflow means 30 adjusts the pressure in the intermediate pressure chamber 23 by causing the lubricating oil in the intermediate pressure chamber 23 to flow out into the suction chamber 16. The fluid outflow means 30 includes a fluid outflow passage 27 formed in the fixed scroll 2 and an intermediate pressure control valve 8 installed in the fluid outflow passage 27. The fluid outflow means 30 may be configured to cause the lubricating oil in the intermediate pressure chamber 23 to flow out into the compression chamber 3.

  The fluid outflow passage 27 includes an intermediate pressure chamber side conduction hole 2p that communicates with the intermediate pressure chamber 23, a suction chamber side conduction hole 2k that communicates with the suction chamber 16 that is the low pressure side of the compression mechanism, and the intermediate pressure chamber side. A valve hole 2h that communicates the conduction hole 2p and the suction chamber side conduction hole 2k is provided.

  The intermediate pressure chamber side conduction hole 2p is constituted by a cylindrical valve seat member 28 press-fitted into the hole of the fixed scroll 2. A valve seat surface 28 a is formed at the edge of the valve seat member 28 on the valve hole side. The valve seat member 28 may be configured by the fixed scroll 2 itself. In that case, the intermediate pressure chamber introduction hole 2p is formed by the hole of the fixed scroll 2 itself.

  The suction chamber side conduction hole 2k communicates with the arcuate groove 2m, and the arcuate groove 2m communicates with the suction hole 2f. The arcuate groove 2m extends in an arc from the suction hole 2f to the side opposite to the suction dig 2e.

  The valve hole 2h is formed so as to extend from the bottom of the large-diameter valve cap insertion portion 2l formed from the back side of the fixed scroll 2. The valve cap insertion portion 21 is closed with a valve cap 8d.

  The intermediate pressure control valve 8 changes the amount of restriction with respect to the fluid flowing through the fluid outflow passage 27 in accordance with the change in the pressure state, and in the low pressure state, the pressure in the intermediate pressure chamber 23 is a first pressure suitable for the low pressure state. In the high pressure state, the pressure in the intermediate pressure chamber 23 is controlled to the second pressure suitable for the high pressure state.

  The intermediate pressure control valve 8 includes a valve body 8a formed of a disc, a valve spring 8b formed of a compression coil spring, and a spring positioning tool formed of a cylinder having an outer diameter slightly larger than the inner diameter of the valve spring 8b. 8c and a valve cap 8d formed of a cylinder having an outer diameter slightly larger than the inner diameter of the valve cap insertion portion 2l.

The valve body 8a is movably disposed in the valve hole 2h of the fluid outflow passage 27, and is disposed so as to be able to contact a valve seat surface 28i provided in the middle of the fluid outflow passage 27. The valve body 8a is connected to set a throttle amount for the fluid flowing through the fluid outflow passage 27 so that the pressure in the intermediate pressure chamber 23 becomes the first pressure in a state where the valve body 8a is in contact with the valve seat surface 28a. A pore 8e is formed. The communication hole 8e constitutes a valve communication path. The valve spring 8b is for pushing the valve body 8a toward the valve seat surface side, and is disposed in the valve hole 2h. The valve body 8a and the valve cap 8d Is sandwiched between.

  The spring positioning tool 8c is for determining the position of the shaft of the valve body 8a, is attached to the valve cap 8d, and is inserted into the valve spring 8b.

  The valve cap 8d closes the valve cap insertion portion 21 to form a wall surface of the flow passage of the valve hole 2h, and abuts one end of the valve spring 8b.

  The intermediate pressure control valve 8 adjusts the intermediate pressure, which is the pressure in the intermediate pressure chamber 23, by the amount of restriction of the communication hole 8e provided in the valve body 8a and the spring load of the valve spring 8b. Since the orbiting scroll 1 is pressed against the fixed scroll 2 by this adjusted intermediate pressure to perform the compression operation, leakage loss and sliding loss at the end of the scroll wraps 1c and 2o can be reduced, and the compressor efficiency can be improved. .

  If the intermediate pressure in the intermediate pressure chamber 23 is too high, the sliding loss at the tips of the scroll wraps 1b, 2o increases and the compressor efficiency decreases, so it is necessary to adjust to an appropriate pressure. In the heat pump type hot water heater, the points required for performance as a hot water heater are the 65 ° C. hot water storage conditions in the intermediate period (hereinafter referred to as the intermediate 65 ° C. hot water storage conditions) and the 90 ° C. hot water storage conditions in the winter (hereinafter referred to as the winter) Called 90 ° C. hot water storage conditions). Under these hot water storage conditions, since the suction pressure and the discharge pressure are different, the optimum value of the intermediate pressure in the intermediate pressure chamber 23 is different.

  The operation point of the intermediate pressure in the intermediate pressure chamber 23 will be described with reference to FIG.

  First, a conventional intermediate pressure control valve 8 that does not have the communication pores 8e in the valve body 8a will be described. In this conventional intermediate pressure control valve 8, the intermediate pressure in the intermediate pressure chamber 23 is adjusted by the function of only the valve spring 8b. If the intermediate pressure at which the compressor efficiency reaches its peak is α1 (point a) under the 65 ° C hot water storage condition where the differential pressure between the discharge pressure and the suction pressure is ΔP1, the differential pressure between the discharge pressure and the suction pressure is The intermediate pressure of the intermediate pressure chamber 23 under the 90 ° C. hot water storage condition rising to ΔP2 is an extremely high pressure of α2 (point b). For this reason, the sliding loss of the scroll wraps 1b and 2o ends increases, the compressor efficiency decreases, and the performance of the hot water heater as a whole becomes low.

  On the other hand, in the intermediate pressure control valve 8 of the present embodiment in which the communication body 8a is provided with the communication hole 8e, the intermediate pressure of the intermediate pressure chamber 23 is adjusted by the functions of the communication hole 8e and the valve spring 8b. That is, in the intermediate 65 ° C. hot water storage condition in which the differential pressure between the discharge pressure and the suction pressure is ΔP1, the intermediate pressure in the intermediate pressure chamber 23 is set to α1 (point a) only by the throttle amount of the communication hole 8e provided in the valve body 8a. ). At this time, the valve spring 8b does not operate. In the winter 90 ° C. hot water storage condition in which the differential pressure between the discharge pressure and the suction pressure rises to ΔP2, not the communication hole 8e provided in the valve body 8a but the valve spring 8b operates to change the intermediate pressure in the intermediate pressure chamber 23 to α2. It is possible to maintain a lower α3 (point c). In the present embodiment, the intermediate pressure can be controlled differently by the communication hole 8e and the valve spring 8b as described above, and the switching point is the point d.

  Further, in an overload condition where the discharge pressure is high, the conventional intermediate pressure control valve 8 has the point e and the intermediate pressure control valve 8 of the present embodiment has the point f, so that the difference between the two intermediate pressures further increases. It becomes. Therefore, the intermediate pressure control valve 8 of the present embodiment can suppress an excessive increase in the intermediate pressure under the condition that the differential pressure between the suction pressure and the discharge pressure becomes large, and the efficiency of the compressor and the reliability of the tooth tip of the scroll wrap are improved. Can be secured.

  According to the scroll compressor 50 of the present embodiment, an increase in leakage loss and sliding loss at the ends of the scroll wraps 1b and 2o can be suppressed with a simple configuration under a plurality of pressure conditions that require performance throughout the year. That is, by providing the intermediate pressure control valve 8 having the valve passage 8e to adjust the pressure in the intermediate pressure chamber 23, the orbiting scroll 1 is not excessively pressed against the fixed scroll 2 even if the pressure condition changes, and the low pressure is reduced. Appropriate intermediate pressures are obtained under pressure and high pressure conditions, respectively, and the performance can be greatly improved. In particular, the efficiency improvement range throughout the year can be increased. Next, the performance improvement fee will be described. Since the intermediate pressure is maintained at α1 (point a) in the intermediate 65 ° C hot water storage condition, the performance is the same as that of the conventional structure, but in the winter 90 ° C hot water storage condition, the performance at the intermediate pressure α2 of the conventional structure is 100%. In this case, the performance at the intermediate pressure α3 of the present embodiment is 104%, and the performance is greatly improved. Also, under an overload condition with a high discharge pressure, the current and power required to drive the motor mounted on the compressor are reduced compared to the conventional structure. As a result, the rotation speed of the compressor is limited under a high load condition due to the current limitation of the inverter mounted on the heat pump water heater unit in the past, but in this embodiment, the rotation speed can be increased by approximately 110%. Expansion is also possible. Further, in the present embodiment, since the intermediate pressure chamber 23 and the fluid outflow passage 27 communicate with each other through the communication pore 8e, fine dust such as welding spatter and iron powder existing inside the compressor is communicated with the communication pore. Get out of 8e. As a result, in the conventional structure, fine dust is caught between the valve body 8a and the valve seat surface 28i, resulting in a pressure lower than the set intermediate pressure, increasing the leakage loss at the scroll wrap tip and reducing the performance. Can be solved, and it becomes a highly reliable scroll compressor.

  In the present embodiment, the horizontal scroll compressor 50 has been described, but the same effect can be obtained with a vertical scroll compressor. Furthermore, the present invention can be applied not only to a heat pump water heater but also to a room air conditioner and a scroll compressor for a refrigeration / refrigeration apparatus, and the same effect can be obtained. The performance improvement allowance when this embodiment is employ | adopted as the compressor for room air conditioners is demonstrated. The operating conditions of the compressor include a cooling intermediate condition, an intermediate condition of the heating intermediate condition, a cooling rated condition, and a rated condition of the heating rated condition. Under intermediate conditions with a small pressure difference, the intermediate pressure of the intermediate pressure chamber 23 is determined by the communication pore 8e, and under the rated conditions with a large pressure difference, the intermediate pressure is determined by the valve spring 8b. As a result, the performance is the same as that of the conventional structure under the intermediate conditions, but the performance is improved by about 101 to 101.5% under the rated conditions, which can greatly contribute to the year-round energy consumption efficiency of the room air conditioner. In addition, although the structure of the intermediate pressure control valve 8 of the compressor for room air-conditioners was demonstrated using the structural component of the compressor for heat pump water heaters mentioned above, it is not the same component but the structure suitable for room air-conditioners ( Valve springs, communication pores, etc.)

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIGS. FIG. 6 is a cross-sectional view of the vicinity of the fluid outflow means 30 of the scroll compressor 50 according to the second embodiment of the present invention, and FIG. 7 is a view of the single state of the valve body 8a of FIG. Note that the valve body 8a in FIG. 6 is a cross section taken along the line AA in FIG. The second embodiment is different from the first embodiment in the points described below, and the other points are basically the same as those in the first embodiment, and thus redundant description is omitted.

  In the second embodiment, the valve 8a is provided with a communication groove 8f without the communication pore 8e. The communication groove 8f is formed of a thin groove and communicates the inside and the outside of the valve seat surface 28a and has the same function as the communication pore 8e.

  In the second embodiment, the intermediate pressure is adjusted to an intermediate pressure at which the compressor efficiency reaches a peak by the amount of restriction of the communication groove 8f of the valve body 8a in the intermediate 65 ° C. hot water storage condition, and in the winter 90 ° C. hot water storage condition, the valve spring In 8b, the pressure is adjusted to an intermediate pressure at which the compressor efficiency reaches a peak. Thereby, in the second embodiment, the same effect as in the first embodiment can be obtained. That is, an excessive increase in the intermediate pressure can be suppressed under the condition that the differential pressure between the suction pressure and the discharge pressure becomes large, and the compressor efficiency and the reliability of the scroll wrap tooth tip can be ensured. In the second embodiment, the communication groove 8f is provided on a straight line passing through the center of the valve body 8a. However, the communication groove 8f may be any groove as long as the throttle amount can be determined. Absent.

(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIGS. FIG. 8 is a cross-sectional view of the vicinity of the fluid outflow means 30 of the scroll compressor 50 according to the third embodiment of the present invention, and FIG. 9 is a view of the single state of the valve seat member 28 of FIG. The valve seat member 28 in FIG. 8 has a cross section along the line BB in FIG. The third embodiment is different from the second embodiment in the following points, and the other points are basically the same as those in the second embodiment, and thus redundant description is omitted.

  In the third embodiment, the valve body 8a is not provided with the communication pore 8e and the communication groove 8f, but the communication groove 28b is provided on the valve seat surface 28a of the valve seat member 28. The communication groove 28b is formed of a thin groove and communicates the inside and the outside of the valve seat surface 28a and has the same function as that of the communication groove 8f.

  In the third embodiment, the intermediate pressure is adjusted to an intermediate pressure at which the compressor efficiency reaches a peak by the amount of restriction of the communication groove 28b of the valve seat surface 28a in the intermediate 65 ° C. hot water storage condition, and in the winter 90 ° C. hot water storage condition, The spring 8b is adjusted to an intermediate pressure at which the compressor efficiency reaches a peak. Thereby, in the third embodiment, the same effect as in the second embodiment can be obtained. That is, an excessive increase in the intermediate pressure can be suppressed under the condition that the differential pressure between the suction pressure and the discharge pressure becomes large, and the compressor efficiency and the reliability of the scroll wrap tooth tip can be ensured. In the third embodiment, the communication groove 28b is provided on a straight line passing through the center of the valve seat surface 28a. However, the communication groove 28b may be any groove as long as the amount of restriction can be determined. It doesn't matter.

The longitudinal cross-sectional view of the scroll compressor of 1st Embodiment of this invention. The figure which looked at the single state of the fixed scroll of FIG. 1 from the anti-scroll lap side. The figure which looked at the fixed scroll 2 of FIG. 2 from the scroll wrap side. Sectional drawing of the fluid outflow means vicinity of FIG. The graph of the intermediate pressure at the time of using the scroll compressor of FIG. 1 for a carbon dioxide-compatible heat pump type hot water heater, and an operating pressure condition. Sectional drawing of the fluid outflow means vicinity of the scroll compressor of 2nd Embodiment of this invention. The figure which looked at the single-piece | unit state of the valve body of FIG. 6 from the communicating groove side. Sectional drawing of the fluid outflow means vicinity of the scroll compressor of 3rd Embodiment of this invention. The figure which looked at the single-piece | unit state of the valve-seat member of FIG. 8 from the communicating groove side.

  DESCRIPTION OF SYMBOLS 1 ... Orbiting scroll, 1a ... Base plate, 1b ... Scroll lap, 1c ... Orbiting bearing, 1d ... Bearing holding part, 1e ... Orbiting Oldham groove, 2 ... Fixed scroll, 2a ... Non-orbiting reference plane, 2b ... Surrounding groove, 2c ... Baipai valve, 2d ... Discharge hole, 2e ... Suction hole, 2f ... Suction hole, 2g ... Flow groove, 2h ... Valve hole, 2k ... Suction chamber side conduction hole, 2l ... Valve cap insertion part, 2m ... Arch Groove, 2n ... base plate, 2o ... scroll lap, 2p ... intermediate pressure chamber side conduction hole, 3 ... compression chamber, 4 ... bypass valve plate, 4a ... retainer, 5 ... bypass screw, 6 ... suction pipe, 7 ... suction side Check valve, 7a ... Valve body, 7b ... Valve spring, 8 ... Intermediate pressure control valve, 8a ... Valve body, 8b ... Valve spring, 8c ... Spring positioning tool, 8d ... Valve cap, 8e ... Communication pore (valve connection) Passage), 8f ... communication groove (valve communication passage), 9 ... frame, 9a ... mounting surface 9b: Revolving clamping surface, 9c: Frame side Oldham groove, 9d: Shaft seal, 9e ... Main bearing, 9f ... Thrust surface, 9h ... Distribution groove, 9i ... Oldham ring installation surface, 10 ... Oldham ring, 10a ... Frame side projection , 10b... Swivel protrusion, 11... Shaft, 11a. Shaft oil supply hole, 11b. Main bearing oil supply hole, 11c... Shaft seal oil supply hole, 11d .. sub bearing oil supply hole, 11e. , 12 ... motor, 12a ... rotor, 12b ... stator, 13 ... auxiliary bearing, 14 ... auxiliary bearing support plate, 14a ... vent hole, 14b ... oil guide hole, 15 ... countershaft housing, 16 ... suction chamber, 17 ... fixed Scroll back chamber, 18 ... motor chamber, 19 ... lubricating oil, 20 ... discharge pipe, 21 ... oil storage chamber, 22 ... sealed container, 23 ... intermediate pressure chamber, 24 ... oil supply pipe, 25 ... oil separation plate, 26 ... fixed screw , 27 ... fluid outflow passage, 28 ... valve seat member, 28a ... valve seat, 28b ... communication groove (Benren passage), 30 ... fluid outlet means, 50 ... scroll compressor.

Claims (7)

A fixed scroll having a base plate and a scroll wrap standing on the base plate;
A revolving scroll that forms a suction chamber or a compression chamber between the fixed scroll and the fixed scroll by engaging with the fixed scroll and having a revolving motion while having a base plate and a scroll wrap standing on the base plate;
An intermediate pressure chamber that applies a pressing force to the orbiting scroll toward the fixed scroll;
Fluid inflow means for allowing fluid to flow into the intermediate pressure chamber;
Fluid outflow means for allowing the fluid in the intermediate pressure chamber to flow out into the suction chamber or the compression chamber,
The fluid outflow means includes a fluid outflow passage that connects the intermediate pressure chamber and the suction chamber or the compression chamber, and an intermediate pressure control valve that is provided in the fluid outflow passage and adjusts the pressure of the intermediate pressure chamber. In the scroll compressor provided,
The intermediate pressure control valve changes a throttle amount with respect to the fluid flowing through the fluid outflow passage according to a change in the pressure state, and the first pressure suitable for the low pressure state is set to the pressure in the intermediate pressure chamber in the low pressure state. And controlling the pressure in the intermediate pressure chamber to a second pressure suitable for the high pressure state in a high pressure state.   The intermediate pressure control valve according to claim 1, wherein the intermediate pressure control valve is movably disposed in the fluid outflow passage and is in contact with a valve seat surface provided in the fluid outflow passage. An elastic body that applies a pressing force to the valve seat surface side, and the valve body forms a valve communication path that sets a throttle amount of the first pressure in contact with the valve seat surface. Scroll compressor characterized by.   3. The scroll compressor according to claim 2, wherein the valve communication passage is provided in a central portion of the valve body and includes a communication pore penetrating from the valve seat surface side to the counter valve seat surface side. .   3. The scroll compressor according to claim 2, wherein the valve communication passage is provided on a valve seat surface side of the valve body and is configured by a groove that communicates the inside and the outside of the valve seat surface.   5. The scroll compressor according to claim 4, wherein the groove constituting the valve communication passage is a linear groove extending in a radial direction from a central portion of the valve body.   The intermediate pressure control valve according to claim 1, wherein the intermediate pressure control valve is movably disposed in the fluid outflow passage and is in contact with a valve seat surface provided in the fluid outflow passage. A scroll compressor comprising: an elastic body that applies a pressing force to the valve seat surface side, wherein the valve seat surface forms a valve communication path that sets a throttle amount of the first pressure.   7. The scroll compressor according to claim 1, wherein the scroll compressor is used for a heat pump type water heater, a room air conditioner, or a refrigerator / freezer.

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