JP6913842B2 - Scroll compressor - Google Patents

Description

The present invention relates to a scroll compressor used in an air conditioner, a refrigerator, a blower, a water heater, and the like.

A fixed scroll with a swirl wrap formed on the end plate and a swivel scroll are engaged to form multiple compression chambers, and a constant pressure is applied to the back pressure chamber formed on the back of the swirl scroll to form a fixed scroll wrap upper surface and a swivel scroll support circle. The plate surface slides thrustly, the crank shaft with an eccentric part is connected to the swivel scroll, and the old dam ring is used to prevent rotation and make the swivel movement, thereby compressing while reducing the volume toward the center. Due to recent inverter control in scroll compressors, operating conditions such as operating frequency, temperature, and pressure change variously according to changes in the season and installation environment, and as a result, the swivel scroll is pressed against the fixed scroll. The thrust force also changes greatly.

In FIG. 8, the swivel scroll 101 is pressed against the fixed scroll 103 by the total thrust force F generated by the pressure difference in the crankshaft direction A with respect to the thrust surface 102 of the end plate, and at the same time, the radial pressure perpendicular to the crankshaft direction. Due to the moment generated mainly by the difference, the so-called overturning moment M, the swivel scroll 101 tries to rotate about the eccentric direction B as an axis.

As a result of the overturning moment acting, the thrust force is supported at two points on the outermost peripheral portion of the end plate thrust surface 102 in the direction perpendicular to the acting direction. That is, assuming that the thrust force at each support point is defined as the support thrust force F1 and F2 and the distances from the overturning moment rotation axis are L1 and L2, respectively, F = F1 + F2 and M = F1 × L1-F2 × L2. The relationship is established.

Under operating conditions with a low compression ratio, the total thrust force F is particularly small, and when the smaller of the supporting thrust forces F1 and F2, that is, the minimum thrust force becomes negative, the turning scroll 101 deviates from the fixed scroll 103. As a result, the gap in the seal portion of the compression chamber is widened, a significant decrease in volumetric efficiency and compression efficiency occurs, and in the worst case, local abnormal wear may also occur.

On the other hand, under operating conditions with a high compression ratio, the total thrust force F becomes large and the swivel scroll 101 is strongly pressed against the fixed scroll 103, so that the sliding loss on the thrust surface 102 tends to be relatively large and the mechanical efficiency tends to deteriorate. It may induce deterioration of the sliding state of the thrust surface 102.

Therefore, it is necessary to optimally design two thrust forces, the total thrust force F and the minimum thrust force, so that a wide range of high efficiency and reliability can be realized within the operating range of the compressor, and the back pressure of the swivel scroll 101. Is generally set to an appropriate value to prevent separation of the swivel scroll 101 under a low compression ratio condition and reduce sliding loss under a high compression ratio condition.

Further, the total thrust force F and the minimum thrust force fluctuate even during one rotation of the crankshaft, and the turning scroll 101 is most likely to separate at the crank angle at which the minimum thrust force is minimized in one rotation. A method of controlling the fluctuation of the total thrust force F and the minimum thrust force per rotation has also been devised.

In the conventional configuration described in Patent Document 1 shown in FIG. 9, the overturning moment M is equal to or greater than a predetermined value by providing an oil groove 202 eccentric from the center of the swivel scroll 201 and introduced with high-pressure oil. In the crank angle range where I'm trying.

Japanese Unexamined Patent Publication No. 2008-274964

However, in the conventional configuration, since it is necessary to provide an oil groove near the outer peripheral portion of the thrust surface, if an attempt is made to prevent the oil groove from communicating with the back pressure chamber or the compression chamber at any crank angle, the swivel scroll end plate There was no choice but to design the outer diameter of the compressor to be relatively large, and there was a problem that the compressor became large.

Further, as a result of increasing the outer diameter of the swivel scroll end plate, there is also a problem that the sliding area of the thrust surface increases, the sliding loss increases, and the mechanical efficiency decreases.

The present invention solves the above-mentioned conventional problems, and achieves both prevention of turning scroll separation and reduction of total thrust force while effectively utilizing the thrust surfaces of the turning scroll and the fixed scroll to suppress an increase in the diameter of the turning scroll. Therefore, it is an object of the present invention to provide a scroll compressor which is small in size, highly efficient, and highly reliable.

In order to solve the above-mentioned conventional problems, the scroll compressor of the present invention has a spiral fixed scroll wrap formed upright on one surface of a mirror plate forming a part of the fixed scroll, and a support disk of the swivel scroll. A pair of compression chambers are formed between the two scrolls by meshing with the spiral swirl scroll wraps that stand upright on the scroll, and the swivel scroll continuously shifts from the suction side to the discharge side while being pressed against the fixed scroll. In a scroll compressor whose volume is changed to compress the fluid, the thrust sliding surfaces of the swivel scroll and the fixed scroll are the first thrust surface on the swivel scroll side and the second thrust surface on the fixed scroll side. Is swirled and slid, and at least one swivel recess is provided on the first thrust surface, and at least one fixed recess is provided on the second thrust surface. The overlapping range of the swivel recess and the fixed recess is changed, and a discharge chamber for discharging the compressed gas from the compression chamber is provided on the side surface of the fixed scroll opposite to the swivel scroll. By providing a continuous passage that penetrates the end plate of the fixed scroll and connects to the fixed recess, the pressure of the discharge chamber that discharges the compressed gas from the compression chamber is supplied to the inside of either the swivel recess or the fixed recess. It is characterized by having a structure for scrolling.

As a result, the area of the pressure receiving portion of the swivel scroll formed by the swivel recess and the fixed recess is minimized at the crank angle where the overlapping range of the swivel recess and the fixed recess is the maximum, and the pressure is received at the crank angle where the overlapping range is the minimum. By maximizing the part area, the load applied to the swivel scroll due to the internal pressure of both recesses can be dynamically changed during one rotation of the crank angle, so that the total thrust at any crank angle during one rotation can be changed. The force and minimum thrust force can be set freely.

As a result, in addition to being able to achieve high efficiency and high reliability in a wide operating range that achieves both prevention of turning scroll separation and reduction of total thrust force, the turning recess and fixing recess are designed in any shape. Since it can be compactly installed in any place on the thrust surface, it is possible to effectively utilize the thrust surface and suppress an increase in the diameter of the swivel scroll.

In addition, since it is relatively easy to process the continuous passage, it is possible to realize a compressor having high efficiency and high reliability at a lower cost.

According to the present invention, the thrust surface of the swivel scroll and the fixed scroll is effectively utilized to suppress the increase in the diameter of the swivel scroll, and at the same time, the swivel scroll separation prevention and the total thrust force reduction are achieved. Moreover, it is possible to provide a highly reliable scroll compressor.

Longitudinal sectional view of the scroll compressor according to the first embodiment of the present invention. The figure which shows the compression process of the compression mechanism in Embodiment 1 of this invention. Another diagram showing the compression step of the compression mechanism according to the first embodiment of the present invention. Longitudinal sectional view of the compression mechanism according to the first embodiment of the present invention. Longitudinal sectional view of another compression mechanism of the scroll compressor in the reference example of the present invention. The figure which shows the other compression mechanism of the scroll compressor in the reference example of this invention. The figure which shows the other compression mechanism of the scroll compressor in the reference example of this invention. The figure which shows the compression mechanism in the conventional compressor The figure which shows the other compression mechanism in the conventional compressor

In the first invention, a spiral fixed scroll wrap formed upright on one surface of a mirror plate forming a part of a fixed scroll and a spiral swirl scroll wrap standing upright on a support disk of a swivel scroll are provided with each other. By meshing, a pair of compression chambers are formed between both scrolls, and while the swivel scroll is pressed against the fixed scroll, the scroll compression that continuously shifts from the suction side toward the discharge side and changes in volume to compress the fluid. In the machine, the thrust sliding surface between the swivel scroll and the fixed scroll is formed by swirling and sliding the first thrust surface on the swivel scroll side and the second thrust surface on the fixed scroll side. At least one swivel recess is provided on the thrust surface, and at least one fixed recess is provided on the second thrust surface. As the swivel scroll moves, the overlapping range between the swivel recess and the fixed recess is increased. In addition to having a variable configuration, a discharge chamber for discharging compressed gas from the compression chamber is provided on the side surface of the fixed scroll opposite to the swivel scroll, and the fixed recess penetrates the end plate of the fixed scroll from this discharge chamber. A scroll compressor characterized in that the pressure of the discharge chamber for discharging the compressed gas from the compression chamber is supplied to the inside of either the swivel recess or the fixed recess by providing a continuous passage connected to the scroll compressor. Is.

As a result, the pressure receiving area of the swivel scroll formed by the swivel recess and the fixed recess is minimized at the crank angle where the overlapping range is the maximum, and the pressure receiving portion area is maximized at the crank angle where the overlapping range is the minimum. As a result, the load applied to the swivel scroll due to the internal pressure of both recesses can be dynamically changed during one rotation of the crank angle, so that the total thrust force and the minimum thrust force at any crank angle during one rotation can be obtained. It can be set freely.

As a result, in addition to being able to achieve high efficiency and high reliability in a wide operating range that achieves both prevention of turning scroll separation and reduction of total thrust force, the turning recess and fixing recess are designed in any shape. Since it can be compactly installed in any place on the thrust surface, it is possible to effectively utilize the thrust surface and suppress an increase in the diameter of the swivel scroll.

In addition, since the amount of change in the load applied to the swivel scroll due to the change in the pressure receiving portion area of the swivel scroll formed by the swivel recess and the fixed recess can be secured to the maximum, the total thrust force and the minimum. The degree of freedom in designing the thrust force is increased, and it is possible to correspond to a wider compressor operating range and the design dimensions of the compression mechanism.

In addition, the swivel recess and the fixed recess in the high-pressure atmosphere apply a load in the direction that cancels the force that presses the swivel scroll against the fixed scroll, so the total thrust force becomes relatively small, and high efficiency is improved by reducing the sliding loss of the thrust surface. Easy to achieve.

Further, since the processing of the continuous passage is relatively easy, it is possible to realize a compressor having high efficiency and high reliability at a lower cost.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. The present invention is not limited to this embodiment.

(Embodiment 1)
FIG. 1 is a vertical cross-sectional view of the scroll compressor according to the first embodiment of the present invention.

In FIG. 1, the entire inside of the closed container 1 has a discharge pressure atmosphere communicating with the discharge pipe 2, a motor 3 is arranged in the center thereof, a compression mechanism is arranged in the upper part thereof, and a crankshaft 4 fixed to the rotor 3a of the motor 3 is provided. The main body frame 5 of the compression mechanism that supports one end of the main body frame 5 is fixed to the closed container 1, and the fixed scroll 6 is attached to the main body frame 5.

One end of the oil passage 7 in the spindle direction provided on the crankshaft 4 leads to the oil supply pump device 8, and the other end finally leads to the eccentric bearing 10 of the swivel scroll 9. The swivel scroll 9 that meshes with the fixed scroll 6 to form the compression chamber 11 is composed of a spiral swirl scroll wrap 9a and a lap support disk 9b in which the eccentric bearing 10 is upright, and includes the fixed scroll 6 and the main body frame 5. It is placed between.

The fixed scroll 6 is composed of a mirror plate 6a and a spiral fixed scroll wrap 6b, and a discharge port 12 is arranged in the central portion of the fixed scroll wrap 6b and a suction port 13 is arranged in the outer peripheral portion.

The eccentric shaft 15 arranged at the upper end of the crankshaft 4 eccentrically from the main shaft 14 of the crankshaft 4 is configured to engage and slide with the eccentric bearing 10 of the swivel scroll 9.

The spindle 14 engages and slides with the main bearing 16 of the main body frame 5, and an annular seal member 17 concentric with the main bearing 16 is mounted on the main body frame 5 in a loose state, and the annular seal member 17 is mounted on the main body frame 5. The back chamber 18 having a substantially discharge pressure atmosphere on the inside and the back pressure chamber 19 having an intermediate pressure atmosphere on the outside are partitioned.

The oil sucked up by the refueling pump device 8 is guided through the oil passage 7 of the crankshaft 4 to the internal space 20 formed between the swivel scroll 9 and the eccentric shaft 15, and one is a lap support circle of the swivel scroll 9. It leads to a back pressure chamber 19 formed by being surrounded by a fixed scroll 6 and a main body frame 5 via a throttle portion 21 provided on the back surface of the plate 9b, and passes through a back pressure adjusting valve 22 and an oil supply passage 22a. Is led to the compression chamber 11.

The back pressure adjusting valve 22 has a function of pressing the swivel scroll 9 against the fixed scroll 6 while maintaining an intermediate pressure higher than the suction pressure, and has a lap support disk 9b of the swivel scroll 9, an upper surface of the fixed scroll wrap 6b, and a mirror plate 6a. And the thrust bearing 23 is formed. The other is discharged to the outside of the compression mechanism through the eccentric bearing 10, the back chamber 18, and the main bearing 16.

A check valve device 24 that opens and closes the outlet side of the discharge port 12 is mounted on the anti-wrap side plane of the end plate 6a of the fixed scroll 6, and the check valve device 24 is a thin steel plate lead valve 24a and a valve retainer. It consists of 24b.

The lower end of the crankshaft 4 is supported by a sub-bearing 25 fixed by welding or shrink-fitting in the closed container 1, and can rotate stably. The sub-bearing 25 has a journal bearing configuration, and a part of the oil sucked up by the refueling pump device 8 is supplied to the sub-bearing 25.

The gas compressed by the compression mechanism passes from the discharge chamber 26 on the downstream side of the check valve device 24 to the downward gas flow path 27 provided near the outer peripheral portion of the compression mechanism, and is shown above the rotor 3a as shown by the dotted arrow. Is led to.

Here, the main bearing 16 and the like are merged with the discharged oil after lubrication, and after reaching the lower part of the rotor 3a through the rotor passage 3b provided inside the rotor 3a, the mixed flow of gas and oil is centrifugal force. Collides with the lower coil end of the stator 3c and separates gas and liquid. The gas after gas-liquid separation is guided to the space above the rotor 3a and the space above the stator 3c, which is partitioned by the partition member 28, through the stator passage 3d provided on the outer periphery of the stator 3c, and the compression mechanism. After reaching the upper space of the compression mechanism through an upward gas flow path (not shown) provided in the discharge pipe 2, the gas is discharged from the discharge pipe 2 to the outside of the closed container 1.

2 and 3 are views for explaining a compression process for each crank angle of 90 degrees in the compression mechanism, FIG. 2 is a front view of a combination of a fixed scroll 6 and a swivel scroll 9, and FIG. 3 is a compression mechanism of the compression mechanism. It is an enlarged sectional view. FIGS. 2 (a) and 3 (a) to 2 and 3 show the moment when the first compression chamber 11a formed by the outer wall of the swivel scroll wrap 9a and the inner wall of the fixed scroll wrap 6b confine the intake gas. Compression proceeds in the order of (b), (c), and (d).

The thrust bearing 23 is formed by pressing the first thrust surface 9c of the lap support disk 9b of the swivel scroll 9 against the upper surface of the fixed scroll lap 6b and the second thrust surface 6c composed of the end plate 6a by an axial thrust force. The first thrust surface 9c is provided with a swivel recess 9d, and the second thrust surface 6c is provided with a fixed recess 6d. In FIG. 2, the outer circumference of the lap support disk 9b of the swivel scroll 9 and the swivel recess 9d are indicated by a two-dot chain line.

The swivel recess 9d is always in communication with the internal space 20 filled with high-pressure oil by the communication passage 29 provided in the lap support disk 9b of the swivel scroll 9, and is swiveled by intermittently overlapping the fixed recess 6d. The inside of the recess 9d and the fixing recess 6d is generally filled with high-pressure oil. Further, the fixed recess 6d and the swivel recess 9d do not communicate with the compression chamber 11 or the back pressure chamber 19.

The operation and operation of the scroll compressor configured as described above will be described below.

Among the wide operating range of the compressor, especially under the operating conditions of a low compression ratio, when the minimum thrust force becomes negative, the turning scroll 9 is separated from the fixed scroll 6, and as a result, the gap of the seal portion of the compression chamber 11 is opened. It expands, resulting in a significant reduction in volumetric and compression efficiency, and in the worst case, local abnormal wear can also occur.

On the other hand, under the operating conditions of a high compression ratio, the total thrust force becomes large and the swivel scroll 9 is strongly pressed against the fixed scroll 6, so that the sliding loss on the first thrust surface 9c and the second thrust surface 6c becomes relatively large. The mechanical efficiency tends to deteriorate, and the sliding state of the first thrust surface 9c and the second thrust surface 6c may deteriorate.

Therefore, it is necessary to optimally design two thrust forces, the total thrust force and the minimum thrust force, so that high efficiency and reliability can be realized in a wide operating range, and the pressure in the back pressure chamber 19 is set to an appropriate value. Therefore, a method for preventing the swivel scroll 9 from separating under a low compression ratio condition and reducing the sliding loss on the first thrust surface 9c and the second thrust surface 6c under a high compression ratio condition is generally used. ..

Further, since the total thrust force and the minimum thrust force fluctuate with the pressure fluctuation of the compression chamber 11 even during one rotation of the crankshaft 4, it is possible to appropriately control the fluctuations of the total thrust force and the minimum thrust force. This is the key to improving the efficiency and reliability of the compressor. The configuration of the first embodiment is an example of a method of controlling the fluctuation of the total thrust force and the minimum thrust force.

As shown in FIG. 2, the swivel recess 9d repeats a swivel motion while overlapping and separating from the fixed recess 6d, and as a result, the swivel recess 9d and the fixed recess 6d overlap each other while the crankshaft 4 makes one rotation. The projected area on the first thrust surface 9c, that is, the pressure receiving area of the swivel scroll 9, will fluctuate. Therefore, the thrust force fluctuates due to the superposition of the pressure fluctuation of the compression chamber 11 which is generally determined by the operating conditions and the pressure receiving surface fluctuation of the fixed recess 6d and the swivel recess 9d according to the configuration of the first embodiment.

According to the present invention, the thrust force can be set to an arbitrary fluctuation value by fluctuating the overlapping range of the swirling recess 9d and the fixing recess 6d, which are designed at an arbitrary shape and position and set to a predetermined pressure, and at least. By reducing the total thrust force while maintaining the minimum thrust force, both prevention of overturning under low compression ratio conditions and low sliding loss on the first thrust surface 9c and second thrust surface 6c under high compression ratio conditions are achieved. Therefore, it is possible to realize a highly efficient and highly reliable compressor.

Further, since the swivel recess 9d and the fixed recess 6d can be designed in any shape and compactly provided in any place on the first thrust surface 9c and the second thrust surface 6c, the first thrust surface 9c and the second thrust can be provided compactly. The surface 6c can be effectively used to suppress an increase in the diameter of the swivel scroll 9.

In the first embodiment, the swivel recess 9d and the internal space 20 are communicated with each other, and the inside of the swivel recess 9d and the inside of the fixed recess 6d intermittently communicating with the swivel recess 9d are filled with high-pressure oil. Since it is possible to secure a large amount of fluctuation in the thrust force due to the fluctuation in the pressure receiving area of the swivel scroll 9 formed by the fixed recess 6d and the swivel recess 9d, the degree of freedom in designing the total thrust force and the minimum thrust force is increased. It is possible to correspond to a wider compressor operating range and the design dimensions of the compression mechanism.

Further, since a load is easily applied in the direction in which the swivel scroll 9 is pulled away from the fixed scroll 6 by the fixed recess 6d and the swivel recess 9d in a high-pressure atmosphere, the total thrust force becomes relatively small, and the first thrust surface 9c and the second thrust surface 6c It is easy to achieve high efficiency by reducing the sliding loss of.

In addition, since the inside of the fixed recess 6d and the swivel recess 9d can be filled with oil to constantly supply oil to the first thrust surface 9c and the second thrust surface 6c, the lubrication state is improved and the sealing property of the compression chamber 11 is improved. By securing it, it is possible to improve efficiency and reliability.

The swivel recess 9d and the fixed recess 6d do not necessarily have to completely overlap or separate from each other, and may be designed in consideration of the required total thrust force and minimum thrust force and the configurable location.

Further, in the vertical cross-sectional view of the compression mechanism shown in FIG. 4, the fixed recess 6d is always communicated with the discharge chamber 26 by the communication passage 29 provided in the fixed scroll 6, and discharges a large amount of oil before being separated. The gas is introduced into the swirling recess 9d and the fixed recess 6d.

In this configuration, since the communication passage 29 is relatively easy to process, it is possible to realize a compressor having high efficiency and high reliability at a lower cost.

The oil in the discharge chamber 26 may be selectively guided to the communication passage 29 with an emphasis on oil lubrication on the first thrust surface 9c and the second thrust surface 6c and ensuring the sealing property of the compression chamber 11. As an example, there is a method of providing a counterbore on the discharge chamber 26 side of the communication passage 29 to form an oil trap.

The communication passage 29 does not necessarily have to be opened in the discharge chamber 26, and even if it is opened in the space 30 above the compression mechanism of the discharge gas atmosphere immediately before being discharged from the discharge pipe 2 to the outside of the closed container 1, the workability is good. It's still easy.

Here, a modified example of the present invention will be described.
For example, in the vertical cross-sectional view of the compression mechanism shown in FIG. 5, the swivel recess 9d is a back pressure chamber 19 filled with oil of intermediate pressure by a communication passage 29 provided in the lap support disk 9b of the swivel scroll 9. It is always in communication, and the insides of the swivel recess 9d and the fixed recess 6d are generally filled with intermediate pressure oil.

In this configuration, since the communication passage 29 is relatively easy to process, it is possible to realize a compressor having high efficiency and high reliability at a lower cost.

In addition, since the inside of the fixed recess 6d and the swivel recess 9d can be filled with oil to constantly supply oil to the first thrust surface 9c and the second thrust surface 6c, the lubrication state is improved and the sealing property of the compression chamber 11 is improved. By securing it, it is possible to improve efficiency and reliability.

Further, in the front view of the compression mechanism shown in FIG. 6, the back pressure adjusting valve 22 is always opened in the back pressure chamber 19 at the inlet of the back pressure adjusting valve 22 for the purpose of stabilizing the pressure in the back pressure chamber 19. Is provided with a counterbore 22b, and the fixing recess 6d is always communicated with the counterbore 22b by a communication passage 29. Therefore, the intermediate pressure oil in the back pressure chamber 19 is introduced into the swirling recess 9d and the fixing recess 6d. There is.

In this configuration, the processing of the communication passage 29 is particularly easy, and not only the structure in which the communication passage 29 is provided as shown in FIG. If the design is such that the crank angle faces the back pressure chamber 19 outside the outermost circumference of the support disk 9b, it is not necessary to process the communication passage 29, so that the cost is lower, the efficiency is higher, and the reliability is higher. Compressor can be realized.

In addition, since the inside of the fixed recess 6d and the swivel recess 9d can be filled with oil to constantly supply oil to the first thrust surface 9c and the second thrust surface 6c, the lubrication state is improved and the sealing property of the compression chamber 11 is improved. By securing it, it is possible to improve efficiency and reliability.

Further, in the front view of the compression mechanism shown in FIG. 7, the fixed recess 6d is located between the suction port 13 and the compression chamber 11 by the communication passage 29 provided in the fixed scroll 6, and the suction chamber 31 with constant suction pressure is located. The low-pressure suction gas is introduced into the swirling recess 9d and the fixing recess 6d.

In this configuration as well, the communication passage 29 can be relatively easily processed, or the connection passage 29 can be made unnecessary by the design in which the fixed recess 6d and the suction chamber 31 overlap, resulting in lower cost, higher efficiency, and higher reliability. Compressor can be realized.

Further, since a load is easily applied in the direction in which the swivel scroll 9 is pressed against the fixed scroll 6 by the swivel recess 9d and the fixed recess 6d in a low pressure atmosphere, the pressure fluctuation range is large and the swivel scroll 9 is easily separated from the fixed scroll 6, such as carbon dioxide. Even in a compressor using a relatively high-pressure refrigerant, the minimum thrust force can be sufficiently secured, and high efficiency and high reliability can be realized more effectively.

If the fixed recess 6d and the swivel recess 9d are filled with oil of suction pressure, high efficiency and high reliability can be achieved by improving the lubrication state of the thrust bearing 23 and ensuring the sealing property of the compression chamber 11, and sealing the thrust bearing 23. This can be achieved by using a low-pressure scroll compressor in which the inside of the container 1 has an atmosphere of suction pressure to introduce oil from the lower part of the closed container 1 into the fixed recess 6d and the swirling recess 9d.

As described above, the scroll compressor according to the present invention effectively utilizes the thrust surfaces of the turning scroll and the fixed scroll to suppress the increase in the diameter of the turning scroll, while at the same time preventing the turning scroll from separating and reducing the total thrust force. As a result, it is possible to provide a compact, highly efficient, and highly reliable scroll compressor. Therefore, in addition to air conditioners and heat pump type water heaters that use HFC-based refrigerants, HCFC-based refrigerants, and HFO-based refrigerants, natural refrigerants can be used. It can also be applied to applications such as air conditioners using carbon dioxide and heat pump type water heaters.

1 Closed container 6 Fixed scroll 6a End plate 6b Fixed scroll wrap 6c Second thrust surface 6d Fixed recess 9 Swivel scroll 9a Swivel scroll wrap 9b Wrap support disc 9c First thrust surface 9d Swivel recess 11 Compression chamber 19 Back pressure chamber 23 Thrust bearing 29 consecutive passages

Claims (1)

Both scrolls are made by engaging the spiral fixed scroll wrap formed upright on one side of the end plate that forms part of the fixed scroll and the spiral swirl scroll wrap that stands upright on the support disk of the swivel scroll. In a scroll compressor in which a pair of compression chambers are formed between the scrolls, and the swirl scroll is pressed against the fixed scroll and continuously shifts from the suction side to the discharge side to compress the fluid, the swivel scroll The thrust sliding surface between the fixed scroll and the fixed scroll is formed by swirling and sliding the first thrust surface on the swivel scroll side and the second thrust surface on the fixed scroll side, and at least one on the first thrust surface. One swivel recess is provided, and at least one fixed recess is provided on the second thrust surface, and the overlapping range of the swivel recess and the fixed recess changes according to the swivel motion of the swivel scroll. A discharge chamber for discharging the compressed gas from the compression chamber is provided on the side surface of the fixed scroll opposite to the swivel scroll, and a continuous passage is provided from the discharge chamber through the end plate of the fixed scroll and connected to the fixed recess. The scroll compressor is characterized in that the pressure of the discharge chamber for discharging the compressed gas from the compression chamber is supplied to the inside of either the swivel recess or the fixed recess.

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