JP2011052685A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor capable of improving reliability of a rear shaft without using a separate component such as a reinforcing ring or the like. <P>SOLUTION: This compressor 1 includes a cylinder body 8 having a compression chamber 11, an eccentric shaft part 14 stored inside the compression chamber 11, a crankshaft 5 having a first shaft part 5f and a second shaft part 5r which are arranged across the eccentric shaft part 14, a first head member 9 arranged at one end of the cylinder body 8 to support the first shaft part 5f, a second head member 10 arranged at the other end of the cylinder body 8 to support the second shaft part 5r, and an annular member 15 fitted externally into the eccentric shaft part 14 inside the compression chamber 11. A central position P1 in the axial direction of the eccentric shaft part 14 arranged inside the compression chamber 11 is arranged on a second shaft part 5r side more than a central position P2 in the axial direction of the compression chamber 11 in side view. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a compressor used in home appliances and the like.

  As this type of technology, a rotary compressor is disclosed in which a transmission element part is housed in the upper part of a sealed container and a compression element part is housed in the lower part, and the rotational force of the transmission element part is transmitted to the compression element part by a rotating shaft and driven. (For example, refer to Patent Document 1). The rotating shaft is composed of a front shaft, a pin shaft (eccentric part), and a rear shaft. Since the piston is fitted on the pin shaft, the outer diameter of the rear shaft is set smaller than the outer diameter of the front shaft. For this reason, in order to prevent a reduction in the reliability of the rear shaft, in the rotary compressor of Patent Document 1, a reinforcing ring is inserted and fixed to the rear shaft.

JP 2006-132414 A

  However, the above-described conventional rotary compressor requires a reinforcing ring as a separate part in order to improve the reliability of the rear shaft. For this reason, there has been a problem that the structure of the rotary compressor is complicated, the number of assembling steps is increased, and the manufacturing cost is increased.

  The objective of this invention is providing the compressor which can improve the reliability of a rear shaft, without using another components, such as a reinforcement ring.

A compressor according to a first aspect of the present invention includes a cylinder body having a compression chamber, an eccentric shaft portion accommodated in the compression chamber, a first shaft portion and a second shaft portion disposed so as to sandwich the eccentric shaft portion. A crankshaft having a shaft portion, a first head member disposed at one end of the cylinder body and capable of supporting the first shaft portion, and disposed at the other end of the cylinder body and supporting the second shaft portion A possible second head member and an annular member externally fitted to the eccentric shaft portion inside the compression chamber, and an axial direction of the eccentric shaft portion arranged inside the compression chamber in a side view Is arranged closer to the second shaft portion than the center position in the axial direction of the compression chamber, and the diameter of the first shaft portion is larger than the diameter of the second shaft portion.

In this compressor, in the side view, the central position in the axial direction of the eccentric shaft portion is arranged closer to the second shaft portion side than the central position in the axial direction of the compression chamber, so that the annular member is inclined and the eccentric shaft is inclined. When the distributed load is applied to the annular member, the load load on the first shaft portion side can be increased and the load load on the second shaft portion side can be increased by allowing the load action point on the upper end of the portion to come into contact with each other. Can be reduced. Therefore, since the reliability of the second shaft portion can be improved without using a separate part such as a reinforcing ring, the manufacturing cost of the compressor can be reduced as compared with the conventional case.
In addition, the load on the second shaft portion side can be alleviated even under a condition that the diameter of the first shaft portion is larger than the diameter of the second shaft portion and is unfavorable for maintaining the reliability of the second shaft portion. Meaningful.

A compressor according to a second aspect of the present invention includes a cylinder body having a compression chamber, an eccentric shaft portion accommodated in the compression chamber, a first shaft portion and a second shaft portion disposed so as to sandwich the eccentric shaft portion. A crankshaft having a shaft portion, a first head member disposed at one end of the cylinder body and capable of supporting the first shaft portion, and disposed at the other end of the cylinder body and supporting the second shaft portion A possible second head member and an annular member externally fitted to the eccentric shaft portion inside the compression chamber, and an axial direction of the eccentric shaft portion arranged inside the compression chamber in a side view Is located closer to the second shaft portion than the center position in the axial direction of the compression chamber, and the diameter ratio of the eccentric shaft portion to the second shaft portion is 2.0 or less. .

In this compressor, in the side view, the central position in the axial direction of the eccentric shaft portion is arranged closer to the second shaft portion side than the central position in the axial direction of the compression chamber, so that the annular member is inclined and the eccentric shaft is inclined. When the distributed load is applied to the annular member, the load load on the first shaft portion side can be increased and the load load on the second shaft portion side can be increased by allowing the load action point on the upper end of the portion to come into contact with each other. Can be reduced. Therefore, since the reliability of the second shaft portion can be improved without using a separate part such as a reinforcing ring, the manufacturing cost of the compressor can be reduced as compared with the conventional case.
In addition, the load ratio on the second shaft side is alleviated even when the diameter ratio between the eccentric shaft portion and the second shaft portion is 2.0 or less, which is unfavorable for maintaining the reliability of the second shaft portion. It is more meaningful because it is possible.

A compressor according to a third aspect of the present invention is arranged such that a plurality of cylinder bodies each having a compression chamber, a plurality of eccentric shaft portions housed in each of the compression chambers, and the plurality of eccentric shaft portions are sandwiched therebetween. A crankshaft having a first shaft portion and a second shaft portion, a connecting shaft portion connecting the plurality of eccentric shaft portions, and an outer side of the plurality of cylinder bodies, and supporting the first shaft portion A possible first head member, a second head member arranged outside the plurality of cylinder bodies and capable of supporting the second shaft portion, and a plate-like member arranged between the plurality of cylinder bodies, In the inside of the plurality of compression chambers, an annular member externally fitted to the eccentric shaft portion, and in a side view, the axial direction of the eccentric shaft portion arranged in at least one of the plurality of compression chambers The center position is the axial direction of the compression chamber. Of being disposed in the second shaft portion than the center position, the diameter of the first shaft portion is larger than the diameter of the second shaft portion.

In this compressor, when viewed from the side, the second axial portion is positioned at a central position in the axial direction of the eccentric shaft portion disposed in at least one of the plurality of compression chambers, rather than the central position in the axial direction of the compression chamber. When the distributed load is applied to the annular member by inclining the annular member inside at least one of the plurality of compression chambers and allowing it to contact the load application point at the upper end of the eccentric shaft portion, While being able to increase the load burden to the 1 axial part side, the load burden to the 2nd axial part side can be decreased. Therefore, since the reliability of the second shaft portion can be improved without using a separate part such as a reinforcing ring, the manufacturing cost of the compressor can be reduced as compared with the conventional case.
In addition, the load on the second shaft portion side can be alleviated even under a condition that the diameter of the first shaft portion is larger than the diameter of the second shaft portion and is unfavorable for maintaining the reliability of the second shaft portion. Meaningful.

A compressor according to a fourth aspect of the invention is arranged such that a plurality of cylinder bodies each having a compression chamber, a plurality of eccentric shaft portions accommodated in each of the compression chambers, and the plurality of eccentric shaft portions are sandwiched therebetween. A crankshaft having a first shaft portion and a second shaft portion, a connecting shaft portion connecting the plurality of eccentric shaft portions, and an outer side of the plurality of cylinder bodies, and supporting the first shaft portion A possible first head member, a second head member arranged outside the plurality of cylinder bodies and capable of supporting the second shaft portion, and a plate-like member arranged between the plurality of cylinder bodies, In the inside of the plurality of compression chambers, an annular member externally fitted to the eccentric shaft portion, and in a side view, the axial direction of the eccentric shaft portion arranged in at least one of the plurality of compression chambers The center position is the axial direction of the compression chamber. Of it is disposed in the second shaft portion than the center position, the diameter ratio of the eccentric shaft portion and the second shaft portion 2.0 or less.

In this compressor, when viewed from the side, the second axial portion is positioned at a central position in the axial direction of the eccentric shaft portion disposed in at least one of the plurality of compression chambers, rather than the central position in the axial direction of the compression chamber. When the distributed load is applied to the annular member by inclining the annular member inside at least one of the plurality of compression chambers and allowing it to contact the load application point at the upper end of the eccentric shaft portion, While being able to increase the load burden to the 1 axial part side, the load burden to the 2nd axial part side can be decreased. Therefore, since the reliability of the second shaft portion can be improved without using a separate part such as a reinforcing ring, the manufacturing cost of the compressor can be reduced as compared with the conventional case.
In addition, the load ratio on the second shaft side is alleviated even when the diameter ratio between the eccentric shaft portion and the second shaft portion is 2.0 or less, which is unfavorable for maintaining the reliability of the second shaft portion. It is more meaningful because it is possible.

  As described above, according to the present invention, the following effects can be obtained.

In the first invention, in the side view, the center position in the axial direction of the eccentric shaft portion is disposed closer to the second shaft portion side than the center position in the axial direction of the compression chamber, whereby the annular member is inclined to be eccentric. By allowing the load application point at the upper end of the shaft portion to come into contact with one another, when a distributed load is applied to the annular member, the load on the first shaft portion side can be increased and the load on the second shaft portion side can be increased. The burden can be reduced. Therefore, since the reliability of the second shaft portion can be improved without using a separate part such as a reinforcing ring, the manufacturing cost of the compressor can be reduced as compared with the conventional case.
In addition, the load on the second shaft portion side can be alleviated even under a condition that the diameter of the first shaft portion is larger than the diameter of the second shaft portion and is unfavorable for maintaining the reliability of the second shaft portion. Meaningful.

In the second invention , the annular member is inclined by disposing the central position in the axial direction of the eccentric shaft portion closer to the second shaft portion side than the central position in the axial direction of the compression chamber in a side view. Thus, when the distributed load is applied to the annular member, the load load on the first shaft portion side can be increased and the second shaft portion side can be increased. It is possible to reduce the load burden. Therefore, since the reliability of the second shaft portion can be improved without using a separate part such as a reinforcing ring, the manufacturing cost of the compressor can be reduced as compared with the conventional case.
In addition, the load ratio on the second shaft side is alleviated even when the diameter ratio between the eccentric shaft portion and the second shaft portion is 2.0 or less, which is unfavorable for maintaining the reliability of the second shaft portion. It is more meaningful because it is possible.

In the third aspect, the central position in the axial direction of the eccentric shaft portion arranged in at least one of the plurality of compression chambers is more than the central position in the axial direction of the compression chamber in a side view. When the distributed load is applied to the annular member by disposing the annular member inside the at least one of the plurality of compression chambers so that the annular member is allowed to abut against the load application point at the upper end of the eccentric shaft portion by being arranged on the biaxial portion side. Moreover, while being able to increase the load burden to the 1st axial part side, the load burden to the 2nd axial part side can be decreased. Therefore, since the reliability of the second shaft portion can be improved without using a separate part such as a reinforcing ring, the manufacturing cost of the compressor can be reduced as compared with the conventional case.
In addition, the load on the second shaft portion side can be alleviated even under a condition that the diameter of the first shaft portion is larger than the diameter of the second shaft portion and is unfavorable for maintaining the reliability of the second shaft portion. Meaningful.

In the fourth aspect, the central position in the axial direction of the eccentric shaft portion disposed in at least one of the plurality of compression chambers is more than the central position in the axial direction of the compression chamber in a side view. When the distributed load is applied to the annular member by disposing the annular member inside the at least one of the plurality of compression chambers so that the annular member is allowed to abut against the load application point at the upper end of the eccentric shaft portion by being arranged on the biaxial portion side. Moreover, while being able to increase the load burden to the 1st axial part side, the load burden to the 2nd axial part side can be decreased. Therefore, since the reliability of the second shaft portion can be improved without using a separate part such as a reinforcing ring, the manufacturing cost of the compressor can be reduced as compared with the conventional case.
In addition, the load ratio on the second shaft side is alleviated even when the diameter ratio between the eccentric shaft portion and the second shaft portion is 2.0 or less, which is unfavorable for maintaining the reliability of the second shaft portion. It is more meaningful because it is possible.

It is an elevation view sectional view of the rotary compressor concerning a 1st embodiment of the present invention. FIG. 2 is a cross-sectional view taken along line 2-2 in FIG. 1. FIG. 3 is a cross-sectional view taken along line 3-3 in FIG. 1. It is the figure which expanded the part enclosed with the dashed-dotted line of FIG. It is explanatory drawing which showed the comparative example of the present Example. It is a first explanatory diagram for explaining the influence of φ _{E /} φ _R. It is a second explanatory diagram for explaining the influence of φ _{E /} φ _R. It is a third explanatory diagram for explaining the influence of φ _{E /} φ _R. It is an elevation view sectional view of the rotary compressor concerning a 2nd embodiment of the present invention. It is the figure which expanded the part enclosed with the dashed-dotted line of FIG. It is explanatory drawing which showed the compressor which concerns on the modification of this invention. It is explanatory drawing which showed the compressor which concerns on the modification of this invention. It is explanatory drawing which showed the compressor which concerns on the modification of this invention.

(First embodiment)
Below, the structure of the rotary compressor which concerns on 1st Embodiment of this invention is outlined. FIG. 1 is an elevational sectional view of a rotary compressor according to a first embodiment of the present invention. A rotary compressor 1 shown in FIG. 1 is used as a part of a refrigeration system such as an air conditioner. That is, the air conditioner includes a condenser, an expansion mechanism, an evaporator (not shown), and the rotary compressor 1 described above as main components.

The rotary compressor 1 is configured as a one-cylinder refrigerant rotary compressor, and sucks CO ₂ refrigerant (hereinafter abbreviated as refrigerant) in the air conditioner and discharges it at a predetermined pressure. As shown in the figure, the rotary compressor 1 includes a sealed container 2, and a motor unit 3 and a compression unit 4 accommodated in the sealed container 2 as main components. The motor unit 3 drives the compression unit 4 via the crankshaft 5, and the compression unit 4 sucks, compresses and discharges low-pressure refrigerant from the accumulator 6 shown schematically. The high-pressure refrigerant in the sealed container 2 is discharged to the outside of the rotary compressor 1 through the discharge pipe 7.

  The compression unit 4 includes a crankshaft 5, a cylinder body 8 having a circular hole 8a, a front head 9 (first head member) and a rear head 10 (second head member) disposed at one end and the other end of the cylinder body 8, respectively. ) And a roller 15 (annular member), and the compression chamber 11 is formed by dividing the circular hole 8a by the front head 9 and the rear head 10. The crankshaft 5 includes an eccentric shaft portion 14 accommodated in the compression chamber 11, and a front shaft portion 5f (first shaft portion) and a rear shaft portion 5r (first shaft portion) disposed so as to sandwich the eccentric shaft portion 14. 2 axis part). The front shaft portion 5f and the rear shaft portion 5r are integrally formed, and the eccentric shaft portion 14 is supported so as to be rotatable along the inner peripheral surface 8b of the circular hole 8a. Further, reference numerals 40 and 50 in the drawing respectively indicate a front side thrust part 40 and a rear side thrust part 50 arranged so as to sandwich the eccentric shaft part 14.

Further, the diameter φ _F shown in the figure is the diameter [mm] of the front shaft portion 5f, the diameter φ _E is the diameter [mm] of the eccentric shaft portion 14, and the diameter φ _R is the diameter [mm] of the rear shaft portion 5r. and respectively, in the present embodiment is designed so that the diameter phi _F is larger than the diameter phi _R. The front head 9 and the rear head 10 are provided so as to support the front shaft portion 5f and the rear shaft portion 5r, respectively.

  Reference is now made to FIG. 2 is a cross-sectional view taken along line 2-2 of FIG. As shown in the drawing, a cylindrical roller 15 is fitted on the eccentric shaft portion 14 of the crankshaft 5 inside the compression chamber 11. The inner diameter of the roller 15 is slightly larger than the outer diameter of the eccentric shaft portion 14 (not shown in FIGS. 1 and 2). The vertical length of the roller 15 is slightly smaller than the vertical length of the compression chamber 11 (the distance between the lower end surface of the plate portion 9b of the front head 9 and the upper end surface of the plate portion 10b of the rear head 10). (Not shown in FIG. 1). A blade 16 extends from the outer peripheral surface of the roller 15 in a direction perpendicular to the axial direction of the crankshaft 5. The blade 16 is accommodated via a pair of bushes 18 in a blade accommodating portion 17 that is recessed in the inner peripheral surface 8 b of the cylinder body 8. A supply port 19 for receiving the supply of refrigerant from the accumulator 6 is formed in the vicinity of the blade housing portion 17. A supply pipe 20 (see also FIG. 1) connected to the accumulator 6 is inserted into the supply port 19, and the supply port 19 has a supply port 21 on the inner peripheral surface 8 b of the cylinder body 8.

  Next, please refer to FIG. 1 and FIG. 3 together. 3 is a cross-sectional view taken along line 3-3 in FIG. As shown in FIGS. 1 and 3, the front head 9 is formed in a plate shape, closes the circular hole 8a of the cylinder body 8, and penetrates the front shaft portion 5f. Has a plate portion 9b. The plate portion 9b is provided with a discharge hole 23 for discharging the refrigerant compressed in the compression chamber 11, and a discharge control mechanism for appropriately controlling the discharge of the refrigerant through the discharge hole 23. 24 is attached. Further, the front head 9 is covered with a muffler 25 for reducing noise caused by the pulsation of the refrigerant. The muffler 25 has a muffler discharge hole 26 for discharging the refrigerant discharged from the discharge hole 23 to the outside of the muffler 25.

  Reference is now made to FIG. As schematically indicated by a two-dot chain line in the figure, the discharge hole 23 is located on the opposite side of the supply port 21 and the blade 16. In other words, the front head 9 is rotationally positioned with respect to the cylinder body 8 such that the supply port 21 and the discharge hole 23 sandwich the blade 16 in a plan view of the cylinder body 8 as shown in FIG. . With this configuration, as shown in this figure, when the roller 15 turns while maintaining the contact state with the inner peripheral surface 8b of the cylinder body 8, the blade 16 moves forward and backward with respect to the blade accommodating portion 17, and the cylinder The refrigerant supplied into the main body 8 is compressed. In addition, the thick line arrow in this figure shows the turning direction (rotation direction of the crankshaft 5) of the roller 15. FIG.

  As shown in FIG. 1, the shape of the rear head 10 described above is similar to the main shape of the front head 9. That is, the rear head 10 is formed in a plate shape, and has a plate portion 10b that closes the circular hole 8a of the cylinder body 8 and is formed with a through hole 10a for allowing the rear shaft portion 5r to pass therethrough. Further, lubricating oil (not shown) is stored between the rear head 10 and the sealed container 2.

  Next, the operation of the rotary compressor 1 according to this embodiment will be outlined. In the state of FIG. 2, low-pressure refrigerant is supplied from the supply port 19 through the supply port 21 into the compression chamber 11. In this state, when the eccentric shaft portion 14 (crankshaft 5) rotates clockwise in the drawing and the eccentric shaft portion 14 passes the supply port 21 in the circumferential direction, the pressure of the refrigerant starts to increase. When the pressure exceeds the set pressure set using the discharge control mechanism 24 shown in FIG. 1, the discharge control mechanism 24 opens and high-pressure refrigerant is discharged into the muffler 25 through the discharge hole 23. Is done. The high-pressure refrigerant discharged into the muffler 25 is silenced in the muffler 25 and then discharged from the compression unit 4 through the muffler discharge hole 26. The high-pressure refrigerant compressed in the compression unit 4 passes through the motor unit 3 and is eventually discharged to the outside of the rotary compressor 1 through the discharge pipe 7 provided in the sealed container 2.

  Reference is now made to FIG. 4 is an enlarged view of a portion surrounded by a one-dot chain line in FIG. FIG. 5 shows a comparative example of this embodiment. In FIG. 4, illustration of the discharge holes 23 and the discharge control mechanism 24 is omitted. In FIG. 4, the difference between the inner diameter of the roller 15 and the outer diameter of the eccentric shaft portion 14 and the difference between the vertical length of the roller 15 and the vertical length of the compression chamber 11 are exaggerated. Further, an arrow L shown in FIG. 4 indicates a distributed load (compressed gas reaction force) acting on the roller 15, and a central position P1 shown in FIG. 4 is lower than the upper end surface of the eccentric shaft portion 14 in the side view. The positions are equidistant from any of the end faces. 4 indicates a position that is equidistant from both the lower end surface of the plate portion 9b of the front head 9 and the upper end surface of the plate portion 10b of the rear head 10 in a side view.

  As shown in FIG. 4, in a side view, the central position P1 in the axial direction of the eccentric shaft portion 14 disposed inside the compression chamber 11 is more axial than the central position P2 in the axial direction of the compression chamber 11. Is disposed at a position shifted to the rear shaft portion 5r side by a distance ΔP. According to such a configuration, when the distributed load L acts on the roller 15, a rotational moment is generated with respect to the roller 15, and the roller 15 is inclined with respect to the eccentric shaft portion 14. The roller 15 in an inclined state comes into contact with the load acting point A1 at the upper end of the eccentric shaft portion 14, and the roller 15 and the eccentric shaft portion 14 make local metal contact at the load acting point A1. When the central position P1 of the eccentric shaft portion 14 is not clear, the central position of the portion where the eccentric shaft portion 14 and the roller are actually in contact with each other and sliding is determined from the central position P2 in the axial direction of the compression chamber 11. In addition, the same effect can be obtained by disposing at a position shifted to the rear shaft portion 5r side.

  In FIG. 4, the state where the roller 15 is inclined is exaggerated from the actual state. Further, as shown in FIG. 4, the load application point A1 is disposed at a position closer to the front shaft portion 5f than the rear shaft portion 5r when viewed from the center position P1 in a side view. This means that the load application point A1 has moved to the front shaft portion 5f side with respect to a load application point A2 of a comparative example described later. Therefore, in the rotary compressor 1 of the present embodiment, it is possible to increase the load on the front shaft portion 5f side and to the rear shaft portion 5r side as compared with the conventional rotary compressor (see FIG. 5). The load of the load can be reduced.

  On the other hand, in the conventional rotary compressor according to the comparative example shown in FIG. 5, the central position P3 in the axial direction of the eccentric shaft portion arranged inside the compression chamber in the side view is the axial direction of the compression chamber. Is coincident with the central position P4. According to such a configuration, the load application point A2 when the distributed load L is applied to the roller is disposed at the same position as the central position P3 in a side view, and the front shaft portion and the load shaft when viewed from the central position P3. It is arranged at the same position from any of the rear shaft portions. Therefore, in the conventional rotary compressor, the load burden distributed to the front shaft portion side is equal to the load burden distributed to the rear shaft portion side.

  Next, a description will be given of the point where the present invention is particularly effective under conditions that are disadvantageous for maintaining the reliability of the rear shaft portion 5r. More specifically, when the following formula (1) is satisfied and the conditions are unfavorable for the reliability of the rear shaft portion 5r, the effect of reducing the load on the rear shaft portion 5r becomes more significant.

φ_Ｅ：偏心軸部１４の直径［ｍｍ］、φ_Ｒ：リア軸部５ｒの直径［ｍｍ］

φ _E : Diameter of eccentric shaft portion 14 [mm], φ _R : Diameter of rear shaft portion 5r [mm]

Hereinafter, it will be described that satisfying the above expression (1) results in an unfavorable condition for the reliability of the rear shaft portion 5r. Please refer to FIGS. FIG. 6 is a first explanatory diagram for explaining the influence of φ _E / φ _R. FIG. 7 is a second explanatory diagram for explaining the influence of φ _E / φ _R. FIG. 8 is a third explanatory diagram for explaining the influence of φ _E / φ _R.

  That is, the damage pattern of the front head 9 and the rear head 10 of the rotary compressor 1 is, for example, as follows. During high differential pressure operation, the shaft bends due to the operational differential pressure, causing the bearing and the shaft to tilt. When tilt occurs, the oil film between the shaft and the bearing becomes thin, and metal contact is likely to occur. Ease of metal contact is determined by the load generated by the amount of tilt and the operating differential pressure. When metal contact occurs, the coefficient of friction increases, and the amount of heat generated at the bearing increases. The amount of heat generation increases as the rotational speed increases. There is a PV value (surface pressure × speed) as a guide for knowing the magnitude of the calorific value. The relationship between the PV value and the cooling by the oil around the bearing portion determines whether or not the bearing is damaged. If the PV value is large and the amount of cooling by oil is small, the probability of bearing damage increases.

That is, (1) a region having a high load value and (2) a region having a high PV value. The technique of this application improves bearing reliability by reducing a load value and PV value. With the parameters shown below (see also FIG. 6), the loads and PV values of the front head 9 and the rear head 10 of the rotary compressor were calculated. The results are summarized as shown in FIG. 7 (load) and FIG. 8 (PV value). 7 and 8, it can be seen that the load and the PV value increase in the region where φ _E / φ _R is 2 or less. That is, in the region where φ _E / φ _R is 2 or less, it is a condition that is disadvantageous for the reliability of the rear shaft portion 5r.

-Diameter d [mm] of the rear shaft portion 5r = 8.0 to 28.0
-Thickness t [mm] of roller 15 = 2.0 to 8.0
Step β [mm] = 0.0 to 0.4
-Thickness Hc [mm] of cylinder body 8 = 6.0 to 16.0
-Effective bearing length L [mm] of the rear head 10 = 6.0 to 25.0
・ Operating differential pressure ΔP [MPa] = 3.0
・ Operation speed N [Hz] = 90.0

[Features of Rotary Compressor of First Embodiment]
As described above, in the rotary compressor 1 of the first embodiment, the central position P1 in the axial direction of the eccentric shaft portion 14 is closer to the rear shaft portion 5r side than the central position P2 in the axial direction of the compression chamber 11 in side view. By disposing the roller 15, the roller 15 is inclined and allowed to come into contact with each other at the load application point A1 at the upper end of the eccentric shaft portion 14, thereby reducing the load burden on the rear shaft portion 5r side. Therefore, since the reliability of the rear shaft portion 5r can be improved without using another component such as a reinforcing ring, the manufacturing cost of the rotary compressor 1 can be reduced as compared with the conventional case.

Moreover, in the rotary compressor 1 of 1st Embodiment, it is disadvantageous for the reliability maintenance of the rear shaft part 5r like the case where the diameter (phi) _F of the front shaft part 5f is designed larger than the diameter (phi) _R of the rear shaft part 5r. Even under the conditions, the load on the rear shaft 5r side can be reduced, which is more meaningful.

  In the rotary compressor 1 according to the first embodiment, the load on the rear shaft portion 5r side is maintained even under a condition that is unfavorable for maintaining the reliability of the rear shaft portion 5r as in the case where the above formula (1) is satisfied. It is more meaningful because the burden can be eased.

(Second Embodiment)
Next, a second embodiment of the present invention will be described. FIG. 9 is an elevational sectional view of a rotary compressor according to the second embodiment of the present invention. Here, it demonstrates centering on the point which is different from the said 1st Embodiment, and the description is abbreviate | omitted about the overlapping point. Members common to the rotary compressor 1 according to the first embodiment and the rotary compressor 101 according to the second embodiment are denoted by the same reference numerals.

  First, the rotary compressor 1 according to the first embodiment is configured as a one-cylinder refrigerant rotary compressor, whereas the rotary compressor 101 according to the second embodiment is a two-cylinder refrigerant rotary compressor. It is configured. In the first embodiment, only one cylinder body 8 is provided, but in this embodiment, two cylinder bodies 8 are arranged in parallel in the axial direction of the crankshaft 5. A middle plate 28 (plate member) is interposed between the two cylinder bodies 8 arranged side by side.

  The eccentric shaft portion 14 is accommodated in each of the two cylinder bodies 8 arranged in parallel. That is, the crankshaft 5 includes two eccentric shaft portions 14. In this embodiment, in order to distinguish these two eccentric shaft portions 14, reference numeral 30 is given to the two eccentric shaft portions 14 closer to the motor portion 3, and reference numeral 31 is assigned to the one farther from the motor portion 3. It was attached. That is, the crankshaft 5 includes a front eccentric shaft portion 30, a rear eccentric shaft portion 31, and a front shaft portion 5f (first shaft portion) disposed so as to sandwich the front eccentric shaft portion 30 and the rear eccentric shaft portion 31. And the rear shaft portion 5r (second shaft portion) and the middle shaft portion 29 (connection shaft portion). The front shaft portion 5f and the rear shaft portion 5r are configured integrally, and these front shaft portions A cylindrical roller 15 (annular member) is fitted on the eccentric portion 30 and the rear eccentric portion 31 inside each compression chamber 11. Further, reference numerals 40 and 50 in the drawing denote the front thrust portion 40 and the rear thrust portion 50, respectively.

Also, the diameter φ _F shown in the figure is the diameter [mm] of the front shaft portion 5f, the diameter φ _E is the diameter [mm] of the front eccentric shaft portion 30 and the rear eccentric shaft portion 31, and the diameter φ _R is the rear shaft. It indicates diameter parts 5r [mm], respectively, in the present embodiment is designed so that the diameter phi _F is larger than the diameter phi _R. In the first embodiment, the muffler 25 is attached only to the front head 9 (first head member). However, in the present embodiment, the muffler 25 is further attached to the rear head 10 (second head member). Further, the middle shaft portion 29 as a portion of the crankshaft 5 between the two eccentric shaft portions 14 arranged side by side is in a relationship of being loosely inserted into the middle plate 28.

  Next, please refer to FIG. FIG. 10 is an enlarged view of a portion surrounded by a one-dot chain line in FIG. As shown in FIG. 10, in the rotary compressor 101 according to the present embodiment, each central position P1 in the axial direction of the front eccentric portion 30 and the rear eccentric portion 31 disposed inside each compression chamber 11 in a side view. Is arranged at a position shifted from the central position P2 in the axial direction of each compression chamber 11 by a distance ΔP toward the rear shaft portion 5r in the axial direction. According to such a configuration, when the distributed load L acts on each roller 15, the roller 15 can be inclined and can be allowed to hit at the load acting point A <b> 1 at the upper end of the eccentric shaft portion 14 similarly to FIG. 4. Therefore, also in the present embodiment, it is possible to reduce the load burden on the rear shaft portion 5r side as compared with the conventional case.

  As described above, in the rotary compressor 101 of the second embodiment, the reliability of the rear shaft portion 5r can be improved without using separate parts such as a reinforcing ring, as in the rotary compressor 1 of the first embodiment. In comparison, the manufacturing cost of the rotary compressor 101 can be reduced.

Further, in the rotary compressor 101 of the second embodiment, as in the rotary compressor 1 of the first embodiment, the diameter φ _F of the front shaft portion 5f is designed to be larger than the diameter φ _R of the rear shaft portion 5r. Thus, even under conditions that are unfavorable for maintaining the reliability of the rear shaft portion 5r, the load on the rear shaft portion 5r side can be reduced, which is more meaningful.

  Further, in the rotary compressor 101 of the second embodiment, similarly to the rotary compressor 1 of the first embodiment, a condition that is disadvantageous for maintaining the reliability of the rear shaft portion 5r as in the case of satisfying the above expression (1). Even lower, it is more meaningful because the load on the rear shaft 5r side can be reduced.

  As mentioned above, although embodiment of this invention was described based on drawing, it should be thought that a specific structure is not limited to these embodiment. The scope of the present invention is indicated not only by the above description of the embodiments but also by the scope of claims for patent, and further includes all modifications within the meaning and scope equivalent to the scope of claims for patent.

In the first and second embodiments described above, the compressor using the CO ₂ refrigerant has been described. However, the present invention is not limited to this and can be applied to a compressor using a refrigerant other than the CO ₂ refrigerant. is there. In particular, when a refrigerant used at a pressure lower than R410A (low GWP refrigerant) is used, the load on the eccentric shaft portion can be reduced because the refrigerant is at a low pressure, and the sliding length of the eccentric shaft portion can be shortened. It is effective in.

  In the first and second embodiments described above, the example in which the front shaft portion 5f and the rear shaft portion 5r are integrally formed has been described. However, the present invention is not limited thereto, and the front shaft portion 5f and the rear shaft portion 5r are configured. May be configured separately.

  In the first embodiment described above, the blade 16 is formed integrally with the roller 15. However, instead of this, the blade 16 may be formed separately from the roller 15. In such a case, it is considered that the blade 16 is pressed against the outer peripheral surface of the roller 15 by appropriate biasing means such as a compression coil spring.

In the above-described second embodiment, an example in which the present invention is applied to a two-cylinder CO ₂ refrigerant rotary compressor has been described. However, the present invention is not limited to such an embodiment, and three or more cylinders are used. It can also be applied to other compressors.

  In the above-described second embodiment, the central position P1 in the axial direction of the front eccentric portion 30 and the rear eccentric portion 31 is set to the rear axial portion by a distance ΔP from the central position P2 in the axial direction of each compression chamber 11. Although an example of disposing at a position shifted to the 5r side has been described, the present invention is not limited to this. As shown in FIG. 11, only the central position P1 in the axial direction of the front eccentric portion 30 is arranged at a position shifted from the central position P2 in the axial direction of each compression chamber 11 by the distance ΔP toward the rear shaft portion 5r. May be.

  Further, as shown in FIG. 12, only the central position P1 in the axial direction of the rear eccentric portion 31 is shifted to the rear shaft portion 5r side by a distance ΔP from the central position P2 in the axial direction of each compression chamber 11. You may arrange in. Also in these configurations, the load on the rear shaft portion 5r is reduced by inclining the roller 15 and causing the roller 15 to contact at the load acting point A1 at the upper end of the front eccentric portion 30 or the rear eccentric portion 31 in a side view. be able to.

In the first embodiment described above, as shown in FIG. 4, the central position P1 in the axial direction of the eccentric shaft portion 14 is more axial than the central position P2 in the axial direction of the compression chamber 11 in a side view. Although an example in which the distance ΔP is arranged in the direction at a position shifted to the rear shaft portion 5r side has been described, the present invention is not limited to such an embodiment. As shown in FIG. 13, the diameter φ _R [mm] of the rear shaft portion 5r (first shaft portion) is made larger than the diameter φ _F [mm] of the front shaft portion 5f (second shaft portion). When designed, the center position P1 in the axial direction of the eccentric shaft portion 14 is shifted to the front shaft portion 5f side in the axial direction by a distance ΔP from the center position P2 in the axial direction of the compression chamber 11 in a side view. You may arrange in a position. According to such an arrangement, the load of the load on the rear shaft portion 5r can be increased by tilting the roller 15 and causing it to come into contact with each other at the load application point A1 at the lower end of the eccentric shaft portion 14, and also at the front. The load burden on the shaft portion 5f side can be reduced. Therefore, the reliability of the front shaft portion 5f can be improved without using separate parts such as a reinforcing ring.

1, 101 Rotary compressor (compressor)
5 Crankshaft 5f Front shaft (first shaft)
5r Rear shaft (second shaft)
8 Cylinder body 9 Front head (first head member)
10 Rear head (second head member)
11 Compression chambers 14, 30, 31 Eccentric shaft portion 15 Roller (annular member)
28 Middle plate (plate-shaped member)
29 Middle shaft (connection shaft)
40 Front side thrust part 50 Rear side thrust part

Claims (4)

A cylinder body having a compression chamber;
A crankshaft having an eccentric shaft portion housed inside the compression chamber, and a first shaft portion and a second shaft portion disposed so as to sandwich the eccentric shaft portion;
A first head member disposed at one end of the cylinder body and capable of supporting the first shaft portion;
A second head member disposed at the other end of the cylinder body and capable of supporting the second shaft portion;
An annular member externally fitted to the eccentric shaft portion inside the compression chamber;
In a side view, the central position in the axial direction of the eccentric shaft portion disposed inside the compression chamber is disposed closer to the second shaft portion than the central position in the axial direction of the compression chamber. Features compressor. A plurality of cylinder bodies each having a compression chamber;
Connecting the plurality of eccentric shaft portions accommodated in each of the compression chambers, the first shaft portion and the second shaft portion disposed so as to sandwich the plurality of eccentric shaft portions, and the plurality of eccentric shaft portions. A crankshaft having a connecting shaft portion,
A first head member disposed outside the plurality of cylinder bodies and capable of supporting the first shaft portion;
A second head member disposed outside the plurality of cylinder bodies and capable of supporting the second shaft portion;
A plate-like member disposed between the plurality of cylinder bodies;
In the inside of the plurality of compression chambers, an annular member externally fitted to the eccentric shaft portion,
In a side view, the central position in the axial direction of the eccentric shaft portion disposed in at least one of the plurality of compression chambers is disposed closer to the second shaft portion than the central position in the axial direction of the compression chamber. The compressor characterized by being made.   The compressor according to claim 1 or 2, wherein a diameter of the first shaft portion is larger than a diameter of the second shaft portion.   The compressor according to claim 1 or 2, wherein a diameter ratio between the eccentric shaft portion and the second shaft portion is 2.0 or less.

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