JP2018031292A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compact compressor of high efficiency and high reliability by combining prevention of separation of swirling scroll and reduction of total thrust force while suppressing increase in a diameter of the swirling scroll by providing a swirling recessed portion and a fixed recessed portion by effectively utilizing thrust surfaces of the swirling scroll and the fixed scroll.SOLUTION: In a scroll compressor, thrust slide surfaces of a swirling scroll 9 and a fixed scroll 6 are formed by swirling and sliding of a first thrust surface 9c at a swirling scroll 9 side and a second thrust surface 6c at a fixed scroll 6 side, the first thrust surface 9c is provided with at least one swirling recessed portion 9d, and the second thrust surface 6c is provided with at least one fixed recessed portion 6d, and an overlapping range of the swirling recessed portion 9d and the fixed recessed portion 6d is changed in accompany with swirling motion of the swirling scroll 9.SELECTED DRAWING: Figure 3

Description

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

  A fixed scroll with a spiral wrap formed on the end plate and a orbiting scroll are engaged to form a plurality of compression chambers, and a fixed pressure is applied to the back pressure chamber formed on the back of the orbiting scroll so that the upper surface of the fixed scroll wrap and the orbiting scroll support circle The plate surface slides in thrust, the crankshaft with an eccentric part is connected to the orbiting scroll, and the Oldham ring is used to prevent rotation and swirl, thereby compressing while reducing the volume toward the center. In recent scroll compressors, due to inverter control in recent years, operating conditions such as operating frequency, temperature, and pressure change variously with changes in the season and installation environment, and as a result, the orbiting scroll is pressed against the fixed scroll. Thrust force also changes greatly.

  In FIG. 8, the orbiting 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 the thrust surface 102 of the end plate as a boundary, and at the same time, the radial pressure perpendicular to the crankshaft direction. Due to the moment caused by the difference, the so-called rollover moment M, the orbiting scroll 101 tends to rotate about the eccentric direction B as an axis.

As a result of the action of the overturning moment, 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, if the thrust force at each support point is defined as support thrust forces F ₁ and F ₂ and the distances from the rollover moment rotation axis are L ₁ and L ₂ , respectively, F = F ₁ + F ₂ , M = F The relationship of ₁ × L ₁ −F ₂ × L ₂ is established.

Under the operating conditions of the low compression ratio, the total thrust force F is particularly small, and when the smaller one of the support thrust forces F ₁ and F ₂ , that is, the minimum thrust force becomes negative, the orbiting scroll 101 is fixed to the fixed scroll 103. As a result, the clearance between the compression chamber seals is enlarged, resulting in a significant reduction in volumetric efficiency and compression efficiency. In the worst case, local abnormal wear may also occur.

  On the other hand, under the high compression ratio operating condition, the total thrust force F is increased and the orbiting scroll 101 is strongly pressed against the fixed scroll 103, so that the sliding loss on the thrust surface 102 becomes relatively large and the mechanical efficiency tends to deteriorate. Therefore, the sliding state of the thrust surface 102 may be deteriorated.

  Therefore, it is necessary to optimally design the two thrust forces of 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. Generally, a method is used in which both the prevention of separation of the orbiting scroll 101 under the low compression ratio condition and the reduction of the sliding loss under the high compression ratio condition are set by setting to an appropriate value.

  Further, since the total thrust force F and the minimum thrust force fluctuate during one revolution of the crankshaft, the orbiting scroll 101 is most likely to separate at a crank angle at which the minimum thrust force is minimized in one revolution. A method of controlling fluctuations in 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 greater than or equal to a predetermined value by providing an oil groove 202 that is eccentric from the center of the orbiting scroll 201 and into which high-pressure oil is introduced. In the crank angle region, the rollover prevention moment that reduces the rollover moment M is generated to increase the minimum thrust force, and the minimum total thrust force F prevents the orbiting scroll 201 from separating and the sliding loss of the thrust surface is reduced. I am trying.

JP 2008-274964 A

  However, in the conventional configuration, since it is necessary to provide an oil groove in the vicinity of the outer peripheral portion of the thrust surface, if an attempt is made to configure the oil groove so as not to communicate with the back pressure chamber or the compression chamber at any crank angle, the orbiting scroll end plate Therefore, the compressor had to be designed to have a relatively large outer diameter, and the compressor was increased in size.

  Further, as a result of enlarging the outer diameter of the orbiting scroll end plate, there is 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 makes effective use of the thrust surfaces of the orbiting scroll and the fixed scroll to prevent the orbiting scroll from separating while preventing the orbiting scroll from separating and reducing the total thrust force. Accordingly, an object is to provide a scroll compressor that is small, highly efficient, and highly reliable.

  In order to solve the above-described conventional problems, a scroll compressor according to the present invention includes a spiral fixed scroll wrap formed upright on one surface of a mirror plate forming a part of a fixed scroll, and a support disk of the orbiting scroll. And a pair of compression chambers are formed between the two scrolls, and the orbiting scroll is continuously pressed from the suction side to the discharge side while being pressed against the fixed scroll. In the scroll compressor whose volume is changed so as to compress the fluid, the thrust sliding surfaces of the orbiting scroll and the fixed scroll include a first thrust surface on the orbiting scroll side and a second thrust surface on the fixed scroll side. Is formed by swinging and sliding, and at least one turning recess is provided on the first thrust surface, and the second thrust surface is provided with At least one fixing recess is provided, wherein with the orbiting motion of the orbiting scroll, is characterized in that it has a structure in which the overlapping range of the swing concave portion and the fixed concave portion is changed.

  As a result, the pressure receiving area of the orbiting scroll formed by the turning recess and the fixed recess is minimized at the crank angle where the overlapping range between the turning recess and the fixed recess is the maximum, and the pressure receiving pressure is obtained at the crank angle where the overlap range is the minimum. By maximizing the area, the load applied to the orbiting scroll by the internal pressure in both recesses can be changed dynamically during one revolution of the crank angle, so the total thrust at any crank angle during one revolution 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 range of operation that is compatible with prevention of turning scroll separation and total thrust force, the swivel recess and fixed recess are designed in any shape, Since it can be provided compactly in a free place on the thrust surface, it is possible to effectively utilize the thrust surface and suppress an increase in the diameter of the orbiting scroll.

  According to the present invention, by effectively utilizing the thrust surfaces of the orbiting scroll and the fixed scroll and suppressing the increase in the diameter of the orbiting scroll, both the prevention of the orbiting scroll separation and the reduction of the total thrust force are achieved. In addition, a highly reliable scroll compressor can be provided.

The longitudinal cross-sectional view of the scroll compressor in Embodiment 1 of this invention The figure which shows the compression process of the compression mechanism in Embodiment 1 of this invention. The other figure which shows the compression process of the compression mechanism in Embodiment 1 of this invention. The longitudinal cross-sectional view of the compression mechanism in Embodiment 1 of this invention Vertical sectional view of another compression mechanism of the scroll compressor according to Embodiment 1 of the present invention. The figure which shows the other compression mechanism of the scroll compressor in Embodiment 1 of this invention. The figure which shows the other compression mechanism of the scroll compressor in Embodiment 1 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

  According to a first aspect of the present invention, a spiral fixed scroll wrap formed upright on one surface of an end plate forming part of the fixed scroll and a spiral scroll scroll wrap standing upright on a support disk of the orbiting scroll are mutually connected. Scroll compression that forms a pair of compression chambers between the two scrolls and changes the volume to compress the fluid by continuously moving from the suction side to the discharge side while the orbiting scroll is pressed against the fixed scroll The thrust sliding surface of the orbiting scroll and the fixed scroll is formed by orbiting and sliding the first thrust surface on the orbiting scroll side and the second thrust surface on the fixed scroll side. The thrust surface is provided with at least one turning recess, and the second thrust surface is provided with at least one fixing recess, With the pivoting movement of the crawl, a scroll compressor, characterized in that a structure in which the overlapping range of the swing concave portion and the fixed concave portion is changed.

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

  As a result, in addition to being able to achieve high efficiency and high reliability in a wide range of operation that is compatible with prevention of turning scroll separation and total thrust force, the swivel recess and fixed recess are designed in any shape, Since it can be provided compactly in a free place on the thrust surface, it is possible to effectively utilize the thrust surface and suppress an increase in the diameter of the orbiting scroll.

  According to a second aspect of the present invention, in particular, in the scroll compressor of the first aspect, at least one of high-pressure oil and high-pressure gas is introduced into one of the swivel recess and the fixed recess. It is characterized by that.

  As a result, the amount of change in the load applied to the orbiting scroll accompanying the change per revolution of the pressure receiving portion area of the orbiting scroll formed by the orbiting recess and the fixed recess can be maximized. The degree of freedom in designing the minimum thrust force is increased, and it is possible to cope with a wider compressor operating range and design dimensions of the compression mechanism.

In addition, since the load is applied in a direction that cancels the force that presses the orbiting scroll against the fixed scroll due to the orbiting recess and the fixed recess in the high-pressure atmosphere, the total thrust force becomes relatively small, and high efficiency is achieved by reducing the sliding loss on the thrust surface. Easy to realize.

  In a third aspect of the invention, in particular, in the scroll compressor of the second aspect of the invention, the fixed scroll and the orbiting scroll are arranged in a sealed container having an oil reservoir in the lower portion. A communication path for introducing high-pressure oil in an oil reservoir is provided, and the downstream end of the communication path is open to the swivel recess.

  As a result, the internal space of the swivel recess and the fixed recess can be filled with oil, and oil can be constantly supplied to the thrust surface, improving the lubrication state of the thrust surface and ensuring the sealing between the thrust surface and the compression chamber. Can improve efficiency and reliability.

  According to a fourth aspect of the invention, in the scroll compressor of the first aspect of the invention, a back pressure chamber is formed on the opposite side of the orbiting scroll to the orbiting scroll wrap, and either the orbiting recess or the fixed recess is provided. It is characterized in that at least one of oil and gas in the back pressure chamber is introduced into one of the insides.

  As a result, it can be configured without providing an introduction passage from the back pressure chamber to the swiveling recess or the fixed recess, or simply by providing an introduction passage, and the cost can be reduced by reducing the number of processing steps. It is.

  According to a fifth aspect of the invention, in particular, in the scroll compressor of the first aspect of the invention, at least one of low-pressure oil and low-pressure gas is introduced into at least one of the swivel recess or the fixed recess. It is characterized by that.

  As a result, a load is further applied in the direction in which the orbiting scroll is pressed against the fixed scroll by the orbiting concave portion and the fixed concave portion in a low pressure atmosphere, so that a relatively large minimum thrust force can be secured, and the separation of the orbiting scroll is suppressed and high efficiency is achieved. And high reliability can be realized.

  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)
FIG. 1 is a longitudinal sectional view of a scroll compressor according to Embodiment 1 of the present invention.

  In FIG. 1, the entire inside of the sealed container 1 becomes a discharge pressure atmosphere communicating with the discharge pipe 2, a motor 3 at the center, a compression mechanism at the top, and a crankshaft 4 fixed to a rotor 3 a of the motor 3. A main body frame 5 of a compression mechanism that supports one end of the main body frame is fixed to the sealed container 1, and a fixed scroll 6 is attached to the main body frame 5.

  The oil passage 7 in the main shaft direction provided in the crankshaft 4 has one end communicating with the oil supply pump device 8 and the other end finally communicating with the eccentric bearing 10 of the orbiting scroll 9. The orbiting scroll 9 that meshes with the fixed scroll 6 to form the compression chamber 11 includes a spiral orbiting scroll wrap 9a and a wrap support disc 9b in which an eccentric bearing 10 is erected. The fixed scroll 6 and the main body frame 5 It is arranged between.

  The fixed scroll 6 includes an end plate 6a and a spiral fixed scroll wrap 6b. A discharge port 12 is disposed at the center of the fixed scroll wrap 6b, and a suction port 13 is disposed at the outer peripheral portion.

An eccentric shaft 15 that is eccentric from the main shaft 14 of the crankshaft 4 and is disposed at the upper end of the crankshaft 4 is configured to engage and slide with the eccentric bearing 10 of the orbiting scroll 9.

  The main shaft 14 is slidably engaged 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. A back chamber 18 having a substantially discharge pressure atmosphere on the inner side and a back pressure chamber 19 having an intermediate pressure atmosphere on the outer side are partitioned.

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

  The back pressure adjusting valve 22 has a function of pressing the orbiting scroll 9 against the fixed scroll 6 while maintaining an intermediate pressure higher than the suction pressure. 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 an anti-wrap side plane of the end plate 6a of the fixed scroll 6. The check valve device 24 includes a reed valve 24a made of a thin steel plate and a valve presser. 24b.

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

  The gas compressed by the compression mechanism passes through a downward gas passage 27 provided in the vicinity of the outer periphery of the compression mechanism from the discharge chamber 26 on the downstream side of the check valve device 24, and as shown by the dotted arrow in the upper part of the rotor 3a. Led to.

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

  2 and 3 are diagrams 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 the fixed scroll 6 and the orbiting scroll 9, and FIG. It is an expanded 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 orbiting scroll wrap 9a and the inner wall of the fixed scroll wrap 6b closes the suction gas. The 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 wrap support disk 9b of the orbiting scroll 9 against the second thrust surface 6c composed of the upper surface of the fixed scroll wrap 6b and the end plate 6a by an axial thrust force. The first thrust surface 9c is provided with a turning recess 9d, and the second thrust surface 6c is provided with a fixed recess 6d. In FIG. 2, the outer periphery of the wrap support disk 9b of the orbiting scroll 9 and the orbiting recess 9d are indicated by a two-dot chain line.

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

  About the scroll compressor comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  In the operating range of a wide range of compressors, especially under low compression ratio operating conditions, when the minimum thrust force becomes negative, the orbiting scroll 9 separates from the fixed scroll 6, and as a result, the clearance between the seal portions of the compression chamber 11 is reduced. It expands, resulting in significant volumetric and compression efficiency degradation, and in the worst case, local abnormal wear can also occur.

  On the other hand, under the high compression ratio operating conditions, the total thrust force is increased and the orbiting 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 be deteriorated.

  Therefore, it is necessary to optimally design the 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. Thus, generally used is a method for achieving both the prevention of separation of the orbiting scroll 9 under the low compression ratio condition and the reduction of the sliding loss at the first thrust surface 9c and the second thrust surface 6c under the high compression ratio condition. .

  Furthermore, since the total thrust force and the minimum thrust force change with the pressure fluctuation of the compression chamber 11 even during one rotation of the crankshaft 4, the fluctuations in the total thrust force and the minimum thrust force can be appropriately controlled. It becomes the point of high efficiency and high reliability of the compressor. The configuration of the first embodiment is an example of a method for controlling fluctuations in the total thrust force and the minimum thrust force.

  As shown in FIG. 2, the swivel recess 9d repeats the swivel motion while overlapping or moving away from the fixed recess 6d. As a result, the crank swivel 4 makes one rotation while the overlapping swivel recess 9d and the fixed recess 6d The projected area on the first thrust surface 9c, that is, the pressure receiving area of the orbiting scroll 9 varies. Therefore, the thrust force fluctuates due to the superposition of the pressure fluctuation of the compression chamber 11 that is generally determined by the operating conditions and the pressure receiving surface fluctuations 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 the fluctuation of the overlapping range of the swiveling concave portion 9d and the fixed concave portion 6d which are designed to have an arbitrary shape and position and set to a predetermined pressure. The total thrust force is reduced while maintaining the minimum thrust force, thereby preventing overturning under low compression ratio conditions and low sliding loss at the first thrust surface 9c and second thrust surface 6c under high compression ratio conditions. Thus, a highly efficient and highly reliable compressor can be realized.

  Further, since the swivel recess 9d and the fixed recess 6d can be designed in any shape and can be provided compactly in any place of the first thrust surface 9c and the second thrust surface 6c, the first thrust surface 9c and the second thrust surface The diameter of the orbiting scroll 9 can be suppressed by effectively utilizing the surface 6c.

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

  Further, since the load is easily applied in the direction in which the orbiting scroll 9 is pulled away from the fixed scroll 6 by the fixed recess 6d and the orbiting recess 9d in the 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 sliding loss.

  In addition, since the inside of the fixed recess 6d and the swivel recess 9d can be filled with oil and the oil can be constantly supplied 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. Ensuring high efficiency and high reliability is possible.

  Note that the swivel recess 9d and the fixed recess 6d do not necessarily need to be completely overlapped or separated from each other, and may be designed in consideration of the required total thrust force and minimum thrust force and a place where they can be configured.

  In the longitudinal sectional view of the compression mechanism shown in FIG. 4, the fixed recess 6 d is always in communication with the discharge chamber 26 through the communication passage 29 provided in the fixed scroll 6, and discharges containing a large amount of oil before being separated. Gas is introduced into the swivel recess 9d and the fixed recess 6d.

  With this configuration, the processing of the communication passage 29 is relatively easy, so that a compressor with higher efficiency and high reliability can be realized at a lower cost.

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

  The communication passage 29 does not necessarily need to be opened to the discharge chamber 26. Even if the communication passage 29 is opened to the compression mechanism upper space 30 in the discharge gas atmosphere immediately before being discharged from the discharge pipe 2 to the outside of the sealed container 1, workability is improved. It remains easy.

  In the longitudinal cross-sectional view of the compression mechanism shown in FIG. 5, the orbiting recess 9 d has a back pressure chamber 19 filled with intermediate pressure oil by a communication passage 29 provided in the lap support disk 9 b of the orbiting scroll 9. The inside of the turning recess 9d and the fixed recess 6d is almost filled with intermediate pressure oil.

  With this configuration, the processing of the communication passage 29 is relatively easy, so that a compressor with higher efficiency and high reliability can be realized at a lower cost.

  In addition, since the inside of the fixed recess 6d and the swivel recess 9d can be filled with oil and the oil can be constantly supplied 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. Ensuring high efficiency and high reliability is possible.

In the front view of the compression mechanism shown in FIG. 6, the back pressure adjusting valve 22 is always opened at the back pressure chamber 19 to stabilize the pressure of the back pressure chamber 19 at the inlet of the back pressure adjusting valve 22. Is provided with a counterbore 22b, and the fixed recess 6d is always in communication with the counterbore 22b through the communication passage 29, so that intermediate pressure oil in the back pressure chamber 19 is introduced into the swivel recess 9d and the fixed recess 6d. Yes.

  This configuration is particularly easy to process the communication path 29, and is not limited to the configuration in which the communication path 29 as shown in FIG. 6 is provided. The design is such that the fixed recess 6d and the counterbore 22b overlap, and the fixed recess 6d If the design is made to have a crank angle that faces the back pressure chamber 19 outside the outermost periphery of the support disk 9b, it is not necessary to process the communication passage 29, so that the cost is further reduced and the efficiency is high and the reliability is high. Can be realized.

  In addition, since the inside of the fixed recess 6d and the swivel recess 9d can be filled with oil and the oil can be constantly supplied 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. Ensuring high efficiency and high reliability is possible.

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

  In this configuration, the processing of the communication path 29 is relatively easy, or the communication path 29 can be made unnecessary by the design in which the fixed recess 6d and the suction chamber 31 are overlapped, so that the cost is high and the efficiency is high. Can be realized.

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

  If the fixed recess 6d and the swivel recess 9d are filled with oil at the suction pressure, it is possible to improve efficiency and reliability by improving the lubrication state of the thrust bearing 23 and ensuring the sealing performance of the compression chamber 11, and sealing. This can be realized by using a configuration in which the oil in the lower part of the hermetic container 1 is introduced into the fixed recess 6d and the swivel recess 9d by a low-pressure scroll compressor in which the inside of the container 1 has an intake pressure atmosphere.

  As described above, the scroll compressor according to the present invention achieves both prevention of turning scroll separation and reduction of the total thrust force while effectively reducing the diameter of the turning scroll by effectively utilizing the thrust surfaces of the turning scroll and the fixed scroll. Therefore, in addition to air conditioners and heat pump water heaters using HFC refrigerants, HCFC refrigerants, and HFO refrigerants, it is possible to provide a compact, highly efficient and highly reliable scroll compressor. It can also be applied to applications such as air conditioners and heat pump water heaters using carbon dioxide.

DESCRIPTION OF SYMBOLS 1 Airtight container 6 Fixed scroll 6a End plate 6b Fixed scroll wrap 6c Second thrust surface 6d Fixed recessed part 9 Orbiting scroll 9a Orbiting scroll wrap 9b Wrap support disk 9c First thrust surface 9d Orbiting recessed part 11 Compression chamber 19 Back pressure chamber 23 Thrust bearing 29 passage

Claims (5)

A scroll-shaped fixed scroll wrap formed upright on one surface of a mirror plate that forms a part of the fixed scroll and a spiral-type scroll scroll wrap standing upright on the support disk of the orbiting scroll are meshed with each other to form both scrolls. In a scroll compressor that forms a pair of compression chambers between them and changes the volume so as to compress the fluid by continuously moving from the suction side to the discharge side while the orbiting scroll is pressed against the fixed scroll,
The thrust sliding surface of the orbiting scroll and the fixed scroll is formed by orbiting and sliding between the first thrust surface on the orbiting scroll side and the second thrust surface on the fixed scroll side. Is provided with at least one swivel recess,
The second thrust surface is provided with at least one fixed recess,
A scroll compressor characterized in that an overlapping range of the turning recess and the fixed recess changes with a turning motion of the turning scroll. 2. The scroll compressor according to claim 1, wherein at least one of high-pressure oil and high-pressure gas is introduced into one of the swivel recess and the fixed recess. The fixed scroll and the orbiting scroll are arranged in a sealed container having an oil reservoir in the lower part, and the orbiting scroll is provided with a communication path for introducing high-pressure oil in the oil reservoir, and The scroll compressor according to claim 2, wherein a downstream end of the passage is open to the swivel recess. A back pressure chamber is formed on the side of the orbiting scroll opposite to the orbiting scroll wrap, and at least one of oil and gas in the back pressure chamber is provided inside either the orbiting recess or the fixed recess. The scroll compressor according to claim 1, wherein one of the scroll compressors is introduced. 2. The scroll compressor according to claim 1, wherein at least one of low-pressure oil and low-pressure gas is introduced into at least one of the turning recess and the fixed recess.

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