JP5789581B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a compressor that compresses a gas or the like, and more particularly to a scroll compressor that compresses a refrigerant gas for heat exchange used in a refrigerator, a water heater, an air conditioner, or the like.

  Various types of compressors have been proposed as positive displacement compressors, but scroll compressors are often used in refrigerators, water heaters, air conditioners, and the like that use refrigerant gas for heat exchange. A scroll compressor uses a pair of spiral bodies (scrolls) having substantially the same shape, and by fixing one and rotating the other relatively, the volume of the compression chamber formed by the pair of spiral bodies is The refrigerant gas is compressed by making it smaller toward the inner circumference. The feature of this compressor is that it has a small number of parts and has a rotation speed-torque characteristic suitable for variable speed control by an inverter.

  By the way, in order to simplify the configuration of this type of scroll compressor, a configuration in which the discharge valve provided at the discharge port of the fixed scroll is omitted has been proposed and actually put into practical use. In such a scroll compressor that omits the discharge valve, it is not necessary to consider the dead volume of the discharge valve or the valve strength associated with the increase in the valve diameter. Therefore, the hole diameter of the discharge port reduces the flow resistance. From the design point of view, it is a general design guideline to make it as large as possible, and the hole diameter is close to the width of the groove formed between the fixed scroll of the fixed scroll and the orbiting scroll. ing.

  On the other hand, when a discharge port having a large hole diameter as described above is opened in the end plate provided with the fixed scroll discharge port, stress concentration occurs around the discharge port due to the deformation of the end plate. Reliability will be reduced.

  For this reason, in order to ensure the reliability of the end plate of the fixed scroll, it is necessary to increase the strength around the discharge port, and the vicinity of the center of the fixed wrap where the fixed wraps are densely erected, that is, the fixed wrap extension side It is necessary to provide a discharge port closer to the center. However, if this is done, in order for the discharge port to come out from the back on the outer side of the orbiting wrap during the discharge process, the orbiting scroll must be revolved considerably, and pressure loss due to flow path resistance increases and performance degradation occurs. It becomes like this.

  In order to improve performance degradation due to such flow path resistance, for example, Japanese Patent Application Laid-Open No. 10-169574 (Patent Document 1) proposes a technique for reducing pressure loss during the discharge process with a simple configuration.

  In the scroll compressor described in Patent Document 1, as described above, the refrigerant gas flows into the suction chamber from the suction port, and the refrigerant gas is formed in the compression chamber formed between the turning scroll and the fixed scroll by the turning motion of the turning scroll. Is transported while being compressed from the outer peripheral side to the center side and discharged from the discharge port. Then, by providing a step portion that allows refrigerant gas to flow in the vicinity of the discharge port formed near the center of the fixed scroll, the flow path resistance is reduced during the discharge stroke after the formation of the minimum sealed space of the outer-line side compression chamber of the orbiting scroll. I try to reduce it. As described above, in the scroll compressor described in Patent Document 1, a step portion communicating with the discharge port is provided to reduce the flow path resistance during the discharge stroke, thereby reducing the pressure loss during the discharge process. We are trying to improve efficiency.

Japanese Patent Laid-Open No. 10-169574

  By the way, although the flow path resistance can be suppressed in the configuration of Patent Document 1, according to the verification by the present inventors, it has been found that it has the following new problem.

  In the configuration of Patent Document 1, the stepped portion communicating with the discharge port is formed in a form orthogonal to the central axis of the discharge port as a stepped planar recess. For this reason, stress concentration between the stepped portion forming portion and the discharge port is caused by the fact that the stepped portion forming portion is orthogonal, the stepped portion and the discharge port being orthogonally crossed, etc. The shape is easy to occur.

  Therefore, the fixed scroll is deformed by the pressure of the refrigerant gas in the discharge process, resulting in a phenomenon that the performance reliability of the end plate of the fixed scroll is lowered. For example, the dimensional accuracy and position accuracy of each lap of the fixed scroll and the orbiting scroll of this type of scroll compressor are managed on the micron order. Therefore, it has been found that when the end plate of the fixed scroll is deformed, in an extreme case, the fixed scroll wrap and the orbiting scroll lap come into contact with each other and the performance is greatly reduced.

  An object of the present invention is to provide a scroll type compressor having improved reliability by suppressing deformation of the end plate based on the recess for reducing the flow resistance provided on the end plate of the fixed scroll.

  A feature of the present invention is that the fixed scroll has an inclined surface that has an inclined surface inclined from the inner surface of the fixed scroll toward the discharge port formed in the fixed scroll, and the inclined surface is formed in the shape of a side surface formed by a cone. Is located adjacent to the discharge port.

  According to the present invention, since the inner surface of the fixed scroll and the discharge port are connected by the inclined surface formed in the shape of the side surface formed by the cone, the connecting portion has a shape having a larger angle than a right angle and stress. Can be mitigated, and deformation of the fixed scroll due to the pressure of the refrigerant gas can be suppressed.

It is a longitudinal cross-sectional view of the scroll type compressor provided with the compressor part which becomes one Embodiment of this invention. It is sectional drawing which shows the state in which the minimum sealed space was formed of the fixed scroll inner line and the turning scroll outer line of the compressor part shown in FIG. It is the enlarged view to which the discharge outlet vicinity of FIG. 2 was expanded. FIG. 4 is a partial cross-sectional view of the fixed scroll taken along line AA shown in FIG. 3. It is the enlarged view which showed the modification of the discharge outlet in other embodiment of this invention, and expanded the discharge opening vicinity corresponding to FIG. It is the perspective view which showed the enlarged view in FIG. 3 in three dimensions, and abbreviate | omitted the turning scroll.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. However, the present invention is not limited to the following embodiments, and various modifications and application examples are included in the technical concept of the present invention. It is included in the range.

  First, a basic configuration of a scroll compressor to which the present invention is applied and a configuration of an embodiment of the present invention will be described with reference to FIGS. 1 to 4.

  First, the overall configuration of the scroll compressor will be described with reference to FIG. FIG. 1 is a longitudinal sectional view of a scroll compressor. Scroll compressors are used as compressors that compress refrigerant gas for heat exchange, such as refrigerators, water heaters, and air conditioners.

  In FIG. 1, reference number 1 is a sealed container, reference number 2 is a compression mechanism, reference number 3 is a turning scroll, reference number 3a is a spiral wrap of the turning scroll 3, reference number 3b is an end plate of the turning scroll 3, reference Reference numeral 4 is a fixed scroll, reference numeral 4 a is a spiral wrap of the fixed scroll 4, reference numeral 4 b is an end plate of the fixed scroll 4, reference numeral 5 is a crankshaft, reference numeral 6 is rotating the fixed scroll 4 and the crankshaft 5. Frame having bearings, reference numeral 7 is an electric motor part comprising a rotor 15 and a stator 16, reference numeral 8 is an Oldham ring related to a rotation preventing member for preventing rotation of the orbiting scroll and causing orbiting movement, reference numeral 12 is a terminal, Reference numeral 14 is a refrigerant gas suction pipe, and the above is a basic component of the scroll compressor.

  The scroll compressor is configured such that the compression mechanism portion 2 and the electric motor portion 7 are connected and housed in the sealed container 1 via the crankshaft 5. The compression mechanism unit 2 includes a fixed scroll 4, a turning scroll 3, a frame 6, a crankshaft 5, and an Oldham ring 8 as main components.

  The fixed scroll 4 has an end plate 4b and a spiral fixed scroll wrap (hereinafter referred to as a wrap) 4a formed upright in the axial direction on the end plate 4b. The fixed scroll 4 is fastened and fixed to the upper side of the frame 6 by bolts. The outer periphery of the frame 6 is fixed to the sealed container 1, and a bearing 6 a that receives the rotation of the crankshaft 5 is provided at the center of the frame 6.

  A suction port 4 c is provided on the outer peripheral portion of the fixed scroll 4. The suction port 4c is formed to extend vertically from the upper surface (anti-wrap surface) of the end plate 4b. A suction pipe 14 connected to an external cycle is press-fitted into the upper part of the suction port 4c. A check valve 19 is disposed at the suction port 4c so as to be movable in the direction in which the suction port 4c extends. The check valve 19 is pressed from the back by a spring 20 and can come into contact with the end of the suction pipe 14. A discharge port 4d and an inclined recess 4e are formed at the center of the fixed scroll 4. Here, the present embodiment is characterized by the formation of the inclined recess 4e, which will be described in detail later.

  The orbiting scroll 3 has an end plate 3b and a spiral orbiting scroll wrap (hereinafter referred to as a wrap) 3a formed upright in the axial direction on the end plate 3b. The orbiting scroll 3 is installed so as to orbit with respect to the fixed scroll 4. The orbiting movement of the orbiting scroll 3 is revolved without rotating by the Oldham ring 8 which is a rotation preventing member.

  As shown in FIG. 2, the compression mechanism section 2 forms a compression chamber 9 and a suction chamber 10 by the orbiting scroll 3 and the fixed orbiting scroll 4 meshed with the spiral wraps 3 a and 4 a inside. The suction port 4 c of the fixed scroll 4 is configured to communicate with the suction chamber 10.

  The electric motor unit 7 includes a stator 16 and a rotor 15. The stator 16 is fixed in the sealed container 1 by shrink fitting, welding, or the like. The rotor 9 is rotatably arranged in the stator 16 and fixes the crankshaft 5 by press-fitting or the like. Electric power is supplied to the motor unit 7 through the terminal 12. The electric motor unit 7 is supplied with electric power from an inverter device (not shown), and the electric power is controlled by the inverter device (for example, PWM control). Accordingly, the compressor unit 2 is controlled to rotate at a variable speed by the electric motor unit 7 and the flow rate of the refrigerant gas is also adjusted.

  Next, the compression operation of the scroll compressor will be described. 1 and 2, the rotor 15 of the electric motor unit 7 is rotated by a rotational force given by the rotating magnetic field generated by the stator 16. The crankshaft 5 fixed to the rotor 15 rotates as the rotor 15 rotates. The orbiting scroll 3 connected to the crankshaft 5 orbits (revolves) without rotating due to the action of the Oldham ring 8. Due to the orbiting motion of the orbiting scroll 3, the internal pressure decreases, the check valve 19 opens the suction port 4c, and the refrigerant gas is sucked into the compression mechanism section 2 through the suction pipe 14 from the external refrigeration cycle.

  The sucked refrigerant gas reaches the compression chamber 9 from the suction chamber 10 of the fixed scroll 4 through the suction port 4c, and gradually in the compression chamber 9 formed by the wrap 3a of the orbiting scroll 3 and the wrap 4a of the fixed scroll 4. After being compressed, it is discharged into the sealed container 1 from the discharge port 4d. The discharged refrigerant gas cools the motor unit 7 and is supplied from the discharge pipe 17 to the external refrigeration cycle.

  Next, the detailed structure of the compression mechanism part 2 which becomes this embodiment is demonstrated, referring FIG. 2 thru | or FIG.

  FIG. 2 is a cross-sectional view of the scroll compressor of FIG. 1 in which the orbiting scroll 3 and the wraps 3a and 4a of the fixed scroll 4 are engaged with each other, and the minimum sealed space 9a is defined by the fixed scroll inner line side and the orbiting scroll outer line side. A compression chamber is formed, and this state indicates a discharge start state. 3 is an enlarged view of the center portion of the fixed scroll of FIG. 2, and FIG. 4 is a cross-sectional view of the portion indicated by the line AA of the fixed scroll excluding the orbiting scroll of FIG.

  As shown in FIGS. 2 and 3, in the minimum sealed space 9a formed by the orbiting wrap outer line 33a of the wrap 3a of the orbiting scroll 3 and the fixed wrap inner line 44b of the wrap 4a of the fixed scroll 4, the inflow from the suction port 4c. The refrigerant gas thus made is compressed by the orbiting motion of the orbiting scroll 3 and discharged into the sealed container 1 from the discharge port 4d. Similarly, also in the minimum sealed space (not shown) formed by the orbiting wrap extension line 33b and the fixed wrap outer line 44a, the refrigerant gas flowing in from the suction port 4c is compressed by the orbiting motion of the orbiting scroll 3, and alternately It is discharged into the sealed container 1 from the discharge port 4d.

  The hole diameter of the discharge port 4d is designed to be as large as possible so that the flow path resistance due to the refrigerant gas at the time of discharge is reduced. However, the hole diameter is close to the groove width of each of the laps 3a and 4a due to processing restrictions. Moreover, in order to suppress the deformation | transformation of the end plate 4b of the fixed scroll 4 based on the excessive pressure by compression operation, as shown in FIG. 3, the spiral-shaped lap | wrap 4a is set up closely and the rigidity is made high. A part of the opening surface of the discharge port 4d is adjacent to the vicinity of the fixed wrap extension line 44b.

  As shown in FIGS. 3, 4 and 6, an inclined recess 4e is provided in the vicinity of the discharge port 4d. The inclined recess 4e has an inclined surface inclined from the fixed lap tooth bottom surface 44c, which is the inner surface of the fixed scroll 4, toward the discharge port 4d. The inclined surface is recessed at a part of the side surface of the cone as viewed from the discharge port 4d. It is configured as follows. Therefore, the surface of the inclined surface has an arcuate shape. Specifically, it is formed in a shape as shown in the perspective view of FIG.

  Here, in this embodiment, the angle formed by the inclined surface of the inclined recess 4e shown in FIG. 4 and the central axis of the discharge port 4d, in other words, the angle formed by the inclined surface and the fixed lap tooth bottom surface 44c is 45 °. It is set as follows. By doing so, the angle α of the connecting portion formed by the inclined surface and the fixed lap tooth bottom surface 44c can be increased, and it can be expected that the stress concentration is suppressed.

  Further, as can be seen from FIG. 6, since the inclined concave portion 4e is a conical inclined surface, the arc forming portion 4f of the inclined concave portion 4e formed on the fixed lap tooth bottom surface 44c is formed into a circular arc, and the discharge port 4d. The circular arc forming portion 4i of the inclined concave portion 4e formed in the shape of a circle is U-shaped along the peripheral shape of the discharge port 4d with the side surface of the cone cut off. The depth D of the inclined surface and the length L of the inclined surface on the fixed lap tooth bottom surface 44c are determined to be appropriate values in terms of design, but this is appropriately changed according to the specifications of the scroll compressor.

  Further, in the present embodiment, the arc diameter of the arc forming portion 4f formed on the plane of the fixed lap tooth bottom surface 44c when the inclined recess 4e is formed, that is, a virtual for forming the inclined surface of the inclined recess 4e. The diameter of the bottom surface of the cone is shorter than the diameter of the discharge port 4d. The reason why the size is smaller than the discharge port 4d is to match the groove width when the laps 3a and 4a of the orbiting scroll 3 and the fixed scroll 4 are closest to each other. The central axis 4g (conical central axis) of the inclined recess 4e for forming the inclined recess 4e is located within the arc of the discharge port 4d and does not coincide with the axis of the central axis 4h of the discharge port 4d. That is, it is configured to be shifted from the axis of the central axis 4h of the discharge port 4d and to be positioned substantially in parallel. Here, the reason why the central axis 4g (conical central axis) of the inclined recess 4e should not be positioned outside the discharge port 4d is that the inclined recess 4e is located when the central axis 4g of the inclined surface is positioned outside the discharge port 4d. This is because a V-shaped slope along the apex shape of the cone is formed outside the discharge port 4e, and does not become an inclined surface toward the traveling direction of the refrigerant gas at the discharge port 4d.

  The central axis 4g of the inclined recess 4e is an area obtained by extending a line connecting the area where the wrap 4a of the fixed scroll 4 and the discharge port 4d are close to each other and the central axis 4h of the discharge port 4d, as shown in the figure. Above, it is located in the part which satisfies the above-mentioned conditions. In FIG. 3, an extension line (corresponding to line AA) extending from a line connecting the point where the inner line 44b of the wrap 4a and the discharge port 4d substantially overlap with the central axis 4h of the discharge port 4d is a portion satisfying the above-described conditions. It is supposed to be located.

  In the present embodiment, the inclined recess 4e is formed under the conditions as described above, but the basic concept is as follows.

  First, the connecting portion between the inclined surface of the inclined concave portion 4e and the fixed lap tooth bottom surface 44c and the discharge port 4d. It is sufficient that the angle is formed. Therefore, in some cases, the arc diameter of the arc forming portion 4f may be larger than the diameter of the discharge port 4d. In short, any shape may be used as long as the inclined concave portion 4e connected to the fixed lap tooth bottom surface 44c and the discharge port 4d forms a conical outer surface.

  Next, although it is the formation position of the inclination recessed part 4e, although it forms in the position mentioned above in the present Example, the point is that the turning wrap outer line 33a of the wrap 3a of the turning scroll 3 and the wrap 4a of the fixed scroll 4 are fixed. It suffices if the minimum sealed space 9a formed by the wrap inner line 44b is formed and is located closer to the discharge port 4d than the turning wrap outer line 33a and communicates with the discharge port 4d. The reason for this is that the refrigerant gas leaks if the inclined recess 4e extends beyond the lap 3a of the orbiting scroll 3, and the above-described conditions are set to prevent this.

  In this embodiment, the inclined recess 4e is formed by a conical drill having a predetermined angle. When the inclined recess 4e and the discharge port 4d are formed using a drill as described above, it is desirable to first form the inclined recess 4e and then form the discharge port 4d. The reason is that if the drill for forming the inclined recess 4e is inserted after the discharge port 4d is formed first, the drill escapes to the discharge port 4d side without mechanical resistance, and the inclined recess 4e having a good shape cannot be formed. Because there is a fear. However, if there is no problem even if the drill escapes to the discharge port 4d side, the order is not limited to this, and the order may be reversed.

  In the compression mechanism having such a configuration, the stress due to the deformation of the end plate 4b of the fixed scroll 4 caused by the excessive refrigerant gas pressure caused by the compression operation causes the fixed lap tooth bottom surface 44c and the boundary portion between the discharge port 4d and the inclined recess 4e. Occurs at the arc-shaped connection. However, since the fixed lap tooth bottom surface 44c, the discharge port 4d, and the inclined recess 4e are connected by the arc-shaped connecting portion, the angle at the connecting portion is larger than the right angle. For this reason, it is possible to significantly suppress the deformation of the end plate 4b as compared to the stepped step portion as in Patent Document 1, and to obtain a highly reliable scroll compressor.

  That is, the discharge port 4d and the fixed lap tooth bottom surface 44c are connected by an inclined surface forming a conical side surface of the inclined recess 4e. For this reason, the fixed wrap tooth bottom surface 44c, the discharge port 4d, and the inclined surface of the inclined recess 4e are connected so as to draw an arc at the connecting portion. Therefore, the fixed lap tooth bottom surface 44c, the discharge port 4d, and the connecting portion between the inclined recess 4e are formed with an angle larger than a right angle, and the stress concentration can be reduced. As a result, the deformation of the end plate 4b can be significantly suppressed as compared with the stepped step portion as in Patent Document 1, and a highly reliable scroll compressor can be obtained.

  Moreover, in patent document 1, since the level | step-difference part comprised by the step-like plane was formed in the end plate of a fixed scroll, the thickness of the end plate is also reduced stepwise. On the other hand, since the end plate 4b according to the present embodiment is connected by being inclined by the inclined recess 4e, the strength at this portion can be increased as compared with the configuration of Patent Document 1.

  Further, since the inclined concave portion 4e is inclined, the flow path resistance can be reduced by smoothly flowing the refrigerant gas. This is because in the conventional configuration, since the step portion is formed, the refrigerant gas bends and flows, so there is a possibility that the flow path resistance is increased.

  Furthermore, according to the scroll compressor of the present embodiment, the spiral wrap 4a is suppressed by suppressing the deformation of the end plate 4b of the fixed scroll 4 under a plurality of pressure conditions that require performance throughout the year with a simple configuration. The deformation of can also be suppressed. As a result, an increase in leakage loss and sliding loss of the spiral wrap 4a can be suppressed, and the performance can be greatly improved. In particular, the efficiency improvement range throughout the year can be increased.

  Further, in the present embodiment, the central axis 4h of the discharge port 4d and the inclined concave portion central axis 4g of the inclined concave portion 4e do not coincide with each other, that is, the central axis 4g of the discharge port 4d and the inclined concave portion central axis 4g of the inclined concave portion 4e are They are shifted in parallel. However, the same effect can be obtained as long as one of the central axes is inclined and the side surfaces of the cone can be formed substantially even if the central axes are not parallel to each other.

  Moreover, in patent document 1, the shape of the level | step-difference part is larger than the hole diameter of a discharge outlet, and it is a corner | angular part where stress tends to concentrate on the connection surface of both formed after processing a discharge outlet and a level | step difference part. There will be many. For this reason, with the deformation of the fixed scroll due to the pressure of the refrigerant gas generated by the compression operation, there is a problem that stress concentration occurs in a wide range of corners, leading to a decrease in reliability of the end plate. On the other hand, according to the present embodiment, the arc forming portion 4f that forms the inclined concave portion 4e is formed to be smaller than the discharge port 4d. The range becomes small, and a decrease in reliability can be reduced as compared with Patent Document 1.

  For this reason, the deformation of the end plate 4b of the fixed scroll 4 is reduced, the deformation of the fixed scroll wrap itself is also reduced, leakage loss and sliding loss between the wraps due to this deformation can be reduced, and the performance of the compressor part is lowered. Can be deterred.

  Furthermore, in recent years, the carbon dioxide refrigerant used in heat pump water heaters and the like has a pressure three times as high as the R410A refrigerant for room air conditioners, and it is essential to suppress deformation of the end plate 4b of the fixed scroll 4. In addition, as a countermeasure against the recent increase in material prices, it is required to use less material itself. According to the structure which becomes this embodiment, while reducing the pressure loss of discharge port 4d vicinity, the deformation | transformation of the end plate 4b of a fixed scroll can also be reduced, and reliability can be improved. As a result, the amount of material used can be reduced as a result. That is, in Patent Document 1, since the strength decreases due to the presence of the stepped portion, it is necessary to increase the thickness of the end plate, and the amount of material used increases, but according to the structure of this embodiment, the same strength is obtained. This is because the thickness of the end plate can be reduced.

  In the present embodiment, the vertical scroll compressor has been described, but the same effect can be obtained with a horizontal scroll compressor. Furthermore, the present invention can be applied to a heat pump water heater, a room air conditioner, and a scroll compressor for a refrigerator / freezer.

  Next, a scroll compressor according to another embodiment of the present invention will be described with reference to FIG. The same reference numerals as those in the embodiment described in FIG. 3 indicate the same components or components having the same function.

  In this embodiment, as described in Example 1, the basic concept regarding the inclined recess 4e is the same.

  That is, it is a connection portion between the inclined surface of the inclined recess 4e and the fixed lap tooth bottom surface 44c and the discharge port 4d, but the angle of the connection portion between the inclined surface of the inclined recess 4e and the fixed lap tooth bottom surface 44c and the discharge port 4d is perpendicular. It is only necessary to form the above angles. In short, any shape may be used as long as the inclined concave portion 4e connected to the fixed lap tooth bottom surface 44c and the discharge port 4d forms a conical outer surface.

Next, regarding the formation position of the inclined recess 4e, the basic concept regarding the inclined recess 4e is the same in this embodiment as described in the first embodiment. 33a and the minimum closed space 9a formed by the fixed wrap extension 44b of the wrap 4a of the fixed scroll 4 are provided at a position closer to the discharge port 4d than the turning wrap outer line 33a and communicating with the discharge port 4d. It is good if it is.

  In the present embodiment, the discharge port 4k is not a circular discharge port 4d as shown in FIG. 3, but a discharge port 4k having an elliptical shape. In order to suppress deformation of the end plate 4b of the fixed scroll 4, a part of the opening of the discharge port 4k is adjacent to the vicinity of the fixed wrap extension line 44b having high rigidity because the spiral wraps 4a are densely arranged. .

  Similar to the embodiment described above, an inclined recess 4e is provided in the vicinity of the discharge port 4k. The inclined concave portion 4e has an inclined surface inclined from the fixed lap tooth bottom surface 44c toward the discharge port 4k, and this inclined surface is constituted by a part of a conical side surface so as to be recessed as viewed from the discharge port 4k. Therefore, the surface of the inclined surface has an arcuate shape. The depth D of the inclined surface and the length L of the inclined surface on the fixed lap tooth bottom surface 44c are determined to be appropriate values in terms of design, but this is appropriately changed according to the specifications of the scroll compressor.

  Further, the arc forming portion 4f formed on the plane of the fixed lap tooth bottom surface 44c when the inclined recess 4e is formed is formed in a circular arc, and the arc forming portion 4i of the inclined recess 4e formed in the discharge port 4d is It is U-shaped by cutting the side of the cone. The central axis 4g for forming the inclined recess 4e is located in the arc of the discharge port 4k and does not coincide with the axis of the discharge port central axis 4h of the discharge port 4d, that is, the discharge port of the discharge port 4k. It is configured to be shifted from the axis of the central axis 4h.

  Further, the central axis 4g of the inclined recess 4e is an area obtained by extending a line connecting the area where the wrap 4a and the discharge port 4d of the fixed scroll 4 are close to each other and the central axis 4h of the discharge port 4d, as shown in FIG. Above, it is located in the part which satisfies the above-mentioned conditions.

  As in FIG. 4, the discharge port 4d and the fixed lap tooth bottom surface 44c are connected by an inclined surface formed by a conical side surface of the inclined recess 4e.

  In the compression mechanism portion of the modified example having such a configuration, the stress due to the deformation of the end plate 4b of the fixed scroll 4 caused by the excessive refrigerant gas pressure due to the compression operation causes the fixed lap tooth bottom surface 44c, the discharge port 4d, and the inclined recess 4e. It concentrates on the arc-shaped connecting part that becomes the boundary part of However, since the fixed lap tooth bottom surface 44c and the discharge port 4k are connected by the arc-shaped connecting portion of the inclined concave portion 4e, the angle of the connecting portion becomes larger than a right angle. Compared to the stepped step portion, deformation of the end plate 4b can be significantly suppressed, and a highly reliable scroll compressor can be obtained.

  Moreover, in patent document 1, since the level | step-difference part comprised by the step-like plane was formed in the end plate of a fixed scroll, the thickness of the end plate is also reduced stepwise. On the other hand, since the end plate 4b according to the present embodiment is connected by being inclined by the inclined recess 4e, the strength at this portion can be increased as compared with the configuration of Patent Document 1.

  Furthermore, according to the scroll compressor of the present embodiment, the spiral wrap 4a is suppressed by suppressing the deformation of the end plate 4b of the fixed scroll 4 under a plurality of pressure conditions that require performance throughout the year with a simple configuration. The deformation of can also be suppressed. As a result, an increase in leakage loss and sliding loss of the spiral wrap 4a can be suppressed, and the performance can be greatly improved. In particular, the efficiency improvement range throughout the year can be increased.

  Further, in the present embodiment, the central axis 4h of the discharge port 4d and the inclined concave portion central axis 4g of the inclined concave portion 4e do not coincide with each other, that is, the central axis 4g of the discharge port 4d and the inclined concave portion central axis 4g of the inclined concave portion 4e are They are shifted in parallel. However, the same effect can be obtained as long as one of the central axes is inclined and the side surfaces of the cone can be formed substantially even if the central axes are not parallel to each other. In short, it is sufficient that the inclined surface is formed using the side surface of the cone.

  Moreover, in patent document 1, the shape of the level | step-difference part is larger than the hole diameter of a discharge outlet, and it is a corner | angular part where stress tends to concentrate on the connection surface of both formed after processing a discharge outlet and a level | step difference part. There will be many. For this reason, with the deformation of the fixed scroll due to the pressure of the refrigerant gas generated by the compression operation, there is a problem that stress concentration occurs in a wide range of corners, leading to a decrease in reliability of the end plate. On the other hand, according to the present embodiment, the arc forming portion 4f that forms the inclined concave portion 4e is formed to be smaller than the discharge port 4d. The range becomes small, and a decrease in reliability can be reduced as compared with Patent Document 1.

  For this reason, deformation of the end plate 4b of the fixed scroll 4 is reduced, the wrap of the fixed scroll itself is also deformed, leakage loss and sliding loss between the wraps due to this deformation can be reduced, and the performance of the compressor section is reduced. Can be deterred.

  To summarize the present invention, in the present invention, there is an inclined surface inclined from the inner surface of the fixed scroll toward the discharge port formed in the fixed scroll, and the inclined surface is formed in the shape of a side surface formed by a cone. A recess is provided adjacent to the discharge port of the fixed scroll. As a result, the inner surface of the fixed scroll and the discharge port are connected by an inclined surface formed in the shape of a side surface formed by a cone. The deformation of the fixed scroll due to the refrigerant gas pressure can be suppressed.

  In addition, according to the embodiment described above, the shape of the discharge port is exemplified as circular or oval, but other shapes may be used. The shape of the discharge port having an appropriate shape may be selected in accordance with the scroll compressor to be used.

  Moreover, although this embodiment demonstrated as a scroll compressor without a discharge valve, the same effect is acquired even if it has a discharge valve.

  DESCRIPTION OF SYMBOLS 1 ... Sealed container, 2 ... Compression mechanism part, 3 ... Orbiting scroll, 3a ... Orbiting scroll wrap, 3b ... Orbiting scroll end plate, 4 ... Fixed scroll, 4a ... Fixed scroll end, 4b ... Fixed scroll end plate, 4c ... Suction port, 4d ... Discharge port, 4e ... Inclined concave portion, 4f ... Arc forming portion of fixed lap tooth bottom surface, 4g ... Central axis of inclined concave portion, 4h ... Central axis of discharging port, 4i ... Arc forming portion of discharging port, DESCRIPTION OF SYMBOLS 5 ... Crankshaft, 6 ... Frame, 6a ... Bearing, 7 ... Electric motor part, 8 ... Oldham ring, 9 ... Compression chamber, 9a ... Minimum sealed space, 10 ... Suction chamber, 12 ... Terminal, 14 ... Suction pipe, 15 ... Rotor, 16 ... stator, 17 ... discharge pipe, 19 ... check valve, 20 ... spring, 33a ... swirling wrap outer line, 33b ... swirling wrap inner line, 44a ... fixed wrap outer line, 44b ... fixed wrap inner line, 4c ... fixed wrap tooth bottom.

Claims (4)

An orbiting scroll that has an end plate and an orbiting wrap standing on the end plate and performs an orbiting motion without rotating,
A fixed scroll with an end plate and a fixed wrap standing on it;
A compression chamber that meshes with the two wraps and is formed between the scrolls and sucks the working fluid to reduce the volume and transfer the working fluid from the outer peripheral side to the center side;
A discharge port for discharging the working fluid formed near the center of the end plate of the fixed scroll;
Wherein the bottom land of the fixed wrap and provided between the discharge port inclined toward the discharge port, and a slope recess having an inclined surface formed in the shape of the side surface of the conical Rutotomoni,
The central axis of the cone forming the inclined surface is located within a circular arc of the discharge port, substantially parallel to the central axis of the discharge port, and at a position shifted therefrom. Scroll compressor. In the scroll compressor according to claim 1 ,
The scroll compressor according to claim 1, wherein a hole diameter of a bottom surface of the cone forming the inclined surface on a tooth bottom surface of the fixed wrap is shorter than a hole diameter of the discharge port . In the scroll compressor according to claim 1 ,
A scroll compressor characterized in that the discharge port has a circular or elliptical cross section . In the scroll compressor according to claim 1 ,
The scroll compressor according to claim 1, wherein an angle between the inclined surface and the bottom surface of the fixed lap is set to 45 ° or less .

Images