JP5371864B2 - Rolling piston compressor - Google Patents

Description

  The present invention relates to a rolling piston compressor, and more particularly to the structure of a refrigerant suction portion.

  In a general rolling piston compressor, pulsation is generated in the sucked refrigerant by continuously and repeatedly repeating the suction and compression of the refrigerant. In order to attenuate the pulsation of the sucked refrigerant, there is a method of installing a resonance silencer in the refrigerant circuit.

  Some of the cylinders in the compression mechanism and the parts in the vicinity thereof have a sound deadening structure by forming a resonance space and / or a flow path communicating with the resonance space (see Patent Document 1).

  In a rolling piston compressor that uses a refrigerant with a high operating pressure in the compressor, there is a technology that provides a slit that forms a vane groove and a partition wall in the vicinity of the vane groove in order to reduce the occurrence of contact between the vane and the vane groove. Yes (see Patent Document 2).

Japanese Patent Laid-Open No. 11-182474 (page 3-5, FIG. 4-10) JP 2006-112396 A (page 3-7, FIG. 1)

  In the conventional method of installing the resonance silencer in the refrigerant circuit, there are problems such as difficulty in downsizing the entire apparatus and an increase in cost due to an increase in parts.

  In addition, in the case of a structure in which a resonance space and / or a flow path communicating with the resonance space is provided in the cylinder inside the compression mechanism to form a silencing structure, it is necessary to process a thin portion near the refrigerant suction hole of the cylinder. In this case, particularly in the case of a refrigerant having a high operating pressure, there are problems such as a decrease in the performance of the compressor due to processing strain and a decrease in the reliability of the compressor due to mixing of processing burrs into the compression mechanism. Furthermore, there is a problem that a sufficient resonance space and / or a flow path communicating with the resonance space may not be secured due to the dimensional relationship between the cylinder thickness and the refrigerant suction hole diameter.

  Further, when a refrigerant having a high operating pressure is used in a rolling piston compressor, a slit that forms a vane groove and a partition wall in the vicinity of the vane groove is necessary. For this reason, when a silencer structure is provided by providing a resonance space and / or a flow path communicating with the resonance space in the cylinder, there is a problem that the position where the silencer structure is provided may be restricted depending on the position of the slit provided in the cylinder. is there.

  The present invention has been made to solve the above-described problems. When a silencing structure is provided inside the compression mechanism, the flow path and the resonance space communicated from the suction portion to the resonance space without processing the cylinder. It aims at obtaining the rolling piston type compressor which has.

  It is another object of the present invention to obtain a rolling piston compressor having a silencing structure that avoids unnecessary cost increase and is easy to process.

A rolling piston compressor according to the present invention is a rolling piston compressor including a compression mechanism that sucks and compresses refrigerant.
The compression mechanism is
A cylinder having an upper surface, a lower surface, an inner peripheral surface, and an outer peripheral surface, the cylinder having a suction hole that penetrates from the outer peripheral surface to the inner peripheral surface and sucks the refrigerant into the interior;
The cylinder is
A cutout portion formed by cutting out the inner peripheral surface from at least one of the upper surface and the lower surface, and formed so as to overlap at least a part of the suction hole formed in the inner peripheral surface. It has a notch part, It is characterized by the above-mentioned.

  The rolling piston compressor according to the present invention is a cylinder in which the compression mechanism portion has an upper surface, a lower surface, an inner peripheral surface, and an outer peripheral surface, and penetrates the refrigerant from the outer peripheral surface to the inner peripheral surface. A cylinder having a suction hole for sucking, the cylinder being a cutout portion formed by cutting out the inner peripheral surface from at least one of the upper surface and the lower surface, and formed on the inner peripheral surface Since the cutout portion is formed so as to overlap with at least a part of the suction hole, a flow path communicating from the suction hole to at least one of the upper surface and the lower surface of the cylinder is obtained without special processing of the cylinder. be able to.

1 is a longitudinal sectional view showing a rolling piston compressor 100 according to Embodiment 1. FIG. 2 is a perspective view of a cylinder 7 according to Embodiment 1. FIG. 3 is a partially enlarged cross-sectional view of a compression mechanism unit 110 according to Embodiment 1. FIG. FIG. 4 is a partially enlarged cross-sectional view of a compression mechanism unit 110 (another example) according to Embodiment 1. FIG. 5 is a cross-sectional view taken along the line AA in FIG. 4, and is a partially enlarged longitudinal sectional view showing a silencing structure (resonator structure) of the compression mechanism unit 110 according to the first embodiment. 6 is a partially enlarged longitudinal sectional view showing an example of a silencing structure (resonator structure) of a compression mechanism section 110 according to Embodiment 2. FIG. 6 is a partially enlarged longitudinal sectional view showing an example of a silencing structure (resonator structure) of a compression mechanism section 110 according to Embodiment 3. FIG. 6 is a partially enlarged longitudinal sectional view showing an example of a silencing structure (resonator structure) of a compression mechanism section 110 according to Embodiment 3. FIG. 6 is a partially enlarged longitudinal sectional view showing an example of a silencing structure (resonator structure) of a compression mechanism section 110 according to Embodiment 3. FIG. 6 is a partially enlarged longitudinal sectional view showing an example of a silencing structure (resonator structure) of a compression mechanism section 110 according to Embodiment 4. FIG. 6 is a partially enlarged longitudinal sectional view showing an example of a silencing structure (resonator structure) of a compression mechanism section 110 according to Embodiment 4. FIG. 10 is a partially enlarged longitudinal sectional view showing an example of a silencing structure (resonator structure) of a compression mechanism unit 110 according to Embodiment 5. FIG. 10 is a partially enlarged longitudinal sectional view showing an example of a silencing structure (resonator structure) of a compression mechanism unit 110 according to Embodiment 5. FIG.

Embodiment 1 FIG.
FIG. 1 is a longitudinal sectional view showing a rolling piston compressor 100 according to the first embodiment. FIG. 2 is a perspective view of the cylinder 7 according to the first embodiment. FIG. 3 is a partially enlarged cross-sectional view of the compression mechanism unit 110 according to the first embodiment. FIG. 4 is a partially enlarged cross-sectional view of the compression mechanism unit 110 (another example) according to the first embodiment. FIG. 5 is a partially enlarged longitudinal sectional view of the compression mechanism unit 110 according to Embodiment 1, and is a sectional view taken along line AA in FIG.

  Hereinafter, the structure of the rolling piston compressor 100 and the compression mechanism 110 of the rolling piston compressor 100 according to the first embodiment will be described with reference to FIGS. 1 to 5. The rolling piston compressor 100 includes a compression mechanism 110 that sucks and compresses refrigerant (hereinafter also referred to as refrigerant gas, suction gas, suction refrigerant, and suction refrigerant gas).

  A rolling piston compressor 100 as a hermetic compressor is connected to a drive unit 120 by a crankshaft 5 and an electric motor 4 including a rotor 4b and a stator 4a as a drive unit 120 in a casing 2 as a hermetic container. The compressed compression mechanism 110 is accommodated.

  The stator 4 a is fixed to the inner peripheral surface of the casing 2, and the rotor 4 b is fixed to the crankshaft 5 at the center of the casing 2. A lubricating oil 22 is stored at the bottom of the casing 2, and the lower end of the crankshaft 5 is immersed in the lubricating oil 22.

  The compression mechanism unit 110 includes a cylinder 7, a rolling piston 8, an eccentric portion 5a of the crankshaft 5, an upper bearing 9, a lower bearing 10, and the like. The cylinder 7 has a cylindrical shape, and has an upper surface 7h, a lower surface 7i, an inner peripheral surface 7f, and an outer peripheral surface 7g (see FIG. 2). It has a suction hole 7a for sucking refrigerant (suction refrigerant, suction refrigerant gas, suction gas, refrigerant gas) from the outside to the inside. That is, the cylinder 7 has a suction hole 7a that penetrates from the outer peripheral surface 7g to the inner peripheral surface 7f and sucks the refrigerant into the inside.

  The rolling piston 8 rotates along the inner peripheral surface 7f (inner wall surface) which is the inner wall surface of the cylinder 7, thereby compressing the sucked refrigerant. The crankshaft 5 is connected to the rolling piston 8 and transmits a rotational force to the rolling piston 8 by being rotated by the drive unit 120.

  The upper bearing 9 supports the crankshaft 5 and closes the upper surface 7 h of the cylinder 7. The lower bearing 10 supports the crankshaft 5 and closes the lower surface 7 i of the cylinder 7. The crankshaft 5 is supported through the upper bearing 9 and the lower bearing 10.

  The cylinder 7 is fixed to the inner wall of the casing 2, and the rolling piston 8 is eccentrically stored in the cylinder 7. An eccentric portion 5 a of the crankshaft 5 is fitted into the rolling piston 8.

  An upper bearing 9 is attached to the upper surface 7 h (upper end surface) of the cylinder 7. A lower bearing 10 is attached to the lower surface 7 i (lower end surface) of the cylinder 7. The cylinder 7 is closed from above and below by the upper bearing 9 and the lower bearing 10, and a compression chamber 12 is formed between the inner peripheral surface 7 f of the cylinder 7 and the outer wall surface of the rolling piston 8.

  As described above, the cylinder 7 is formed with the refrigerant suction hole 7a communicating with the low pressure chamber 12a of the compression chamber 12 (see FIGS. 3 and 4). The suction hole 7 a communicates with a suction pipe 19 attached to the casing 2.

  The rolling piston 8 is stored eccentrically with respect to the cylinder 7, and rotates while a part of the outer wall surface of the rolling piston 8 is in contact with the inner peripheral surface 7 f of the cylinder 7. As the rolling piston 8 rotates while contacting the inner peripheral surface 7f, the refrigerant gas sucked from the suction hole 7a is compressed in the compression chamber 12, and the compressed refrigerant gas is discharged into the discharge port 7c (see FIGS. 2 to 4). It is discharged from.

  As shown in FIG. 2, the cylinder 7 is formed with a vane groove 7 b extending in the radial direction of the cylinder 7 from between the suction hole 7 a and the discharge port 7 c of the compression chamber 12. The vane groove 7b extends from the compression chamber 12 in the radial direction of the cylinder 7 and penetrates from the upper surface 7h of the cylinder 7 to the lower surface 7i. A vane groove hole 7d is formed at the outer peripheral end of the vane groove 7b (of the cylinder 7). The vane groove hole 7d communicates with the vane groove 7b and penetrates from the upper surface 7h to the lower surface 7i of the cylinder 7 in the same manner as the vane groove 7b.

  As shown in FIGS. 3 and 4, a vane 14 for separating the compression chamber 12 into a low-pressure side low-pressure chamber 12a and a high-pressure side high-pressure chamber 12b is inserted into the vane groove 7b. The vane 14 is pressed to the inner side of the cylinder 7 by, for example, a spring (not shown) accommodated in the vane slot 7d from the back portion (the outer peripheral side of the cylinder 7). The tip of the vane 14 comes into contact with the outer wall surface of the rolling piston 8 by pressing of a spring or the like. In this manner, the compression chamber 12 is separated into the low-pressure side low-pressure chamber 12a and the high-pressure side high-pressure chamber 12b by the vanes 14.

  In the compression process, a compression load P is applied to the vane 14 from the high pressure chamber 12b side, and the vane 14 presses the vane groove 7b to the low pressure chamber 12a side. At this time, the vane 14 and the low-pressure side edge of the vane groove 7b come into contact with each other, so that there is a risk of mechanical loss or the like in the compression mechanism 110 due to wear of the contact portion of the cylinder 7.

  In order to reduce the above-described wear and the like due to the piece contact, a slit portion 15 (an example of a notch portion) that penetrates in the vertical direction is provided on the inner peripheral surface 7f of the cylinder 7 on the low pressure chamber 12a side. The cylinder 7 is formed with a slit portion 15 formed on the inner peripheral surface 7f and penetrating from the upper surface 7h to the lower surface 7i. The slit portion 15 is provided on the low pressure side of the vane groove 7b (see FIGS. 3 and 4), and is provided so as to form a partition wall 16 between the slit portion 15 and the vane groove 7b. Even if the vane 14 presses the low pressure side of the vane groove 7b by such a slit portion 15, the partition wall 16 is elastically bent in the pressing direction. Therefore, the low pressure side of the vane 14 and the vane groove 7b is used. The impact (wear, mechanical loss, etc.) due to the contact with each other can be reduced.

  The cylinder 7 is a slit portion 15 (an example of a notch portion) formed by cutting out the inner peripheral surface 7f from at least one of the upper surface 7h and the lower surface 7i, and a suction hole 7a formed in the inner peripheral surface 7f. The slit portion 15 is formed so as to overlap with at least a part of the slit portion 15. The slit portion 15 described in the present embodiment is formed by notching the inner peripheral surface 7f in the vertical direction from the upper surface 7h to the lower surface 7i.

  The cylinder 7 is provided with a discharge port 7c on the high pressure chamber 12b side in the vicinity of the vane 14 (see FIGS. 2 to 4). The discharge port 7 c communicates with the internal space of the casing 2 through an opening (not shown) provided in the upper bearing 9. A discharge pipe 20 is attached to the upper part of the casing 2, and the high-temperature and high-pressure refrigerant released from the compression mechanism 110 into the internal space of the casing 2 is discharged from the discharge pipe 20 to the outside of the rolling piston compressor 100. Discharged.

  As shown in FIG. 2, in the cylinder 7 according to the present embodiment, the slit portion 15 provided on the inner peripheral surface 7f is positioned so as to overlap the opening portion (inner peripheral surface opening portion 7e) on the inner side of the suction hole 7a. Is formed. In FIG. 2, the slit portion 15 and the inner peripheral surface opening portion 7 e completely overlap. However, at least a part of the slit portion 15 may overlap with the inner peripheral surface opening portion 7 e.

  As shown in FIGS. 3 and 4, the slit portion 15 is a notched portion that is notched in the radial direction of the cylinder 7 from the inner peripheral surface 7 f, and therefore has a recessed portion 40. Since the slit portion 15 overlaps with the suction hole 7a (the inner peripheral surface opening portion 7e thereof), the suction hole 7a and the slit portion 15 communicate with each other.

  As shown in FIG. 5, the upper bearing 9 includes a resonance space 31 (an example of a resonance space part) (an example of a resonance part) that attenuates a pulsation frequency generated from the refrigerant sucked from the suction hole 7 a, a slit part 15, A flow path 32 (an example of a flow path part) (an example of a space part) that communicates with the resonance space 31 is provided. The flow path 32 and the resonance space 31 are formed on the lower end surface of the upper bearing 9 so that the lower end surface of the upper bearing 9 is opened.

  FIG. 5 is a cross-sectional view taken along the line AA of FIG. 4, and is a partially enlarged longitudinal sectional view showing a silencing structure (resonator structure) of the compression mechanism unit 110 according to the first embodiment. The shape indicated by the dotted line in FIG. 4 is a shape when the flow path 32 and the resonance space 31 are viewed from above. The flow path 32 has a rectangular cross section, and a part (tip) of the flow path 32 overlaps with the slit part 15, and communicates with the slit part 15 at this overlapping part. The resonance space 31 that communicates with the flow path 32 has a circular cross section. Therefore, the cross section of the flow path 32 and the resonance space 31 communicating with the flow path 32 has a substantially keyhole shape as shown in FIG. The shape of the cross section of the flow path 32 and the resonance space 31 is not limited to a rectangle or a circle (keyhole shape). The shape is such that the lower end surface of the upper bearing 9 can be easily processed, and any conditions satisfying the relationship (conditions) such as the volume of the resonance space 31 to be described later, the length of the flow path 32 communicating with the resonance space 31, and the cross-sectional area Shape may be sufficient.

  On the lower end surface of the upper bearing 9, a resonance space 31 having a certain volume and a flow path 32 communicating with the resonance space 31 are formed. The flow path 32 is formed at a position where at least a part of the flow path 32 communicates with the slit portion 15 on the lower end surface of the upper bearing 9. Even when the resonance space 31 and the flow path 32 are formed in the lower bearing 10, the configuration is the same as that of the upper bearing 9.

  As shown in FIG. 5, the suction refrigerant gas passes through the suction hole 7a and is sucked into the compression chamber of the cylinder 7 from the inner peripheral surface opening 7e (suction gas route Q1). The suction hole 7a communicates with the resonance space 31 via the flow path 32 that communicates with the slit portion 15 (route Q2). That is, the flow path 32 is formed so as to communicate with the opening formed in the upper surface 7 h of the cylinder 7 above the suction hole 7 a by the slit portion 15. The slit portion 15 is a flow path (communication path) that connects the suction hole 7 a and the resonance space 31 via the flow path 32.

  That is, the slit portion 15 according to the present embodiment communicates the configuration as a slit for reducing the contact between the vane 14 and the vane groove 7b, and the suction hole 7a and the resonance space 31 via the flow path 32. It is the structure which serves as the structure as a flow path to be made. Since the slit for reducing the contact between the vane 14 and the vane groove 7b is a necessary structure for the compression mechanism 110 of the rolling piston compressor 100, the slit 15 according to the present embodiment is provided. Thus, it is possible to obtain a configuration as a flow path that connects the suction hole 7a and the resonance space 31 without performing special processing on the cylinder 7.

  The resonance space 31 and the flow path 32 indicated by dotted lines in FIG. 4 indicate the positions of the resonance space 31 and the flow path 32 formed in the upper bearing 9. In FIG. 4, the flow path 32 and the resonance space 31 are formed right above the suction hole 7a. Like the resonance space 31 and the flow path 32 indicated by dotted lines in FIG. 3, the resonance space 31 and the flow path 32 are not shifted directly above the suction hole 7a but shifted laterally from the position directly above the suction hole 7a. It may be provided at the other position (that is, the upper portion of the portion that is not the suction hole 7a).

  The positions of the resonance space 31 and the flow path 32 may or may not be directly above the suction hole 7a. It suffices that at least a part of the flow path 32 communicates with the slit portion 15 and the position of the resonance space 31 and the flow path 32 does not interfere with the vane groove 7 b and the compression chamber 12.

  The relationship between the upper bearing 9 and the cylinder 7 described above is the same when the resonance space 31 and the flow path 32 (an example of a space portion) are formed in the lower bearing 10.

  Next, the operation will be described. When the rolling piston compressor 100 drives the electric motor 4, the driving force of the electric motor 4 is transmitted to the rolling piston 8 of the compression mechanism unit 110 via the crankshaft 5. Due to this rotational force, the rolling piston 8 rotates eccentrically in the cylinder 7. As a result, the refrigerant gas flows into the low pressure chamber 12a of the compression chamber 12 through the suction hole 7a, is compressed in the high pressure chamber 12b, and the refrigerant gas in the high pressure state is discharged from the discharge port 7c to the internal space of the casing 2, and thereafter The discharge pipe 20 discharges to the refrigeration circuit outside the rolling piston compressor 100.

  When the refrigerant gas passes through the suction hole 7a, the compression mechanism part 110 communicates with the flow path 32 formed in the upper bearing 9 through the slit part 15 provided in the cylinder 7 from the suction hole 7a. It communicates with the resonance space 31 of the volume. During this process, a specific frequency band of the pulsation generated in the suction refrigerant (refrigerant gas) is attenuated. The specific frequency band to be attenuated is determined by the relationship between the volume of the resonance space 31, the length of the flow path 32 communicating with the resonance space 31, and the cross-sectional area.

  In the compression process described above, the vane 14 that protrudes into the compression chamber 12 and separates the low-pressure chamber 12a and the high-pressure chamber 12b while contacting the rolling piston 8 is formed on the low-pressure side of the vane groove 7b by the compression load (P) of the high-pressure refrigerant. Are pressed from the high pressure chamber 12b side to the low pressure chamber 12a side. Here, since the slit portion 15 provided so as to penetrate the inner peripheral surface 7f of the cylinder 7 of the low pressure chamber 12a in the vertical direction forms the partition wall 16 with the vane groove 7b, the partition wall 16 is pressed. It becomes a mechanism which bends elastically in the direction, and the occurrence of per contact between the vane 14 and the vane groove 7b is reduced.

  As described above, the rolling piston compressor 100 according to the present embodiment uses the slit portion 15 of the cylinder 7 that is necessary for reducing the occurrence of contact between the vane 14 and the vane groove 7b in the compression process. Thus, since the silencing structure (resonance space 31, flow path 32) for attenuating the pulsation frequency of the suction refrigerant is formed in the upper bearing 9, the cylinder 7 need not be processed only for the silencing structure. In addition, when processing distortion occurs in the cylinder 7, a refrigerant gas leaks during the compression process due to a change in the clearance between the rolling piston 8, the upper bearing 9, and the lower bearing 10, and the efficiency of the rolling piston compressor 100 decreases. However, according to the rolling piston compressor 100 according to the present embodiment, such a fear can be reduced.

  A resonator that attenuates a specific frequency band by a structure such as the resonance space 31 and the flow path 32 will be described. A device that attenuates a specific frequency band by a structure such as the resonance space 31 and the flow path 32 is called a Helmholtz resonator. The Helmholtz resonator can attenuate the resonance frequency of the resonator.

In the Helmholtz resonator, assuming that the volume of the resonance space 31 is V, the cross-sectional area of the flow path 32 is S, the length of the flow path 32 is L, and the speed of sound is C, the resonance frequency f0 of the resonator is ).
f0 = C / {2π (S / VL) ^1/2 } (Formula 1)

  Further, since the pulsation of the suction refrigerant gas is larger in the lower frequency band, from the above (Equation 1), if the cross-sectional area S of the flow path 32 is constant, the volume V of the resonance space 31 is increased or the flow path 32 By increasing the length L, an effect can be exhibited in a low frequency band.

  According to the rolling piston compressor 100 according to the present embodiment, the resonance space 31 and / or the resonance space 31 are provided in the cylinder 7 because the upper bearing 9 is provided with the resonance space 31 and the flow path 32 communicating with the resonance space. There are fewer restrictions on the shape and size than when the flow path 32 communicating with the flow path 32 is provided.

  Further, according to the rolling piston compressor 100 according to the present embodiment, the resonance space 31 and the flow path 32 communicating with the resonance space can be formed with a simple shape, so the upper bearing 9 is a cast product. In some cases, the silencing structure can be obtained without machining by forming the resonance space 31 and the flow path 32 communicating with the resonance space in advance from the time of molding.

  In the first embodiment, the case where the upper bearing 9 is formed with the resonance space 31 and the flow path 32 communicating with the resonance space has been described. However, the resonance space 31 and the flow path 32 communicating with the resonance space are formed in the lower bearing 10. Even in this case, the same explanation can be applied.

Embodiment 2. FIG.
In the first embodiment, the configuration in which only the upper bearing 9 is provided with the resonance space 31 and the flow path 32 communicating with the resonance space 31 has been described. In the present embodiment, the case where the resonance space 31 and the flow path 32 communicating with the resonance space are formed only in the lower bearing 10 will be described.

  FIG. 6 is a partially enlarged longitudinal sectional view showing an example of a silencing structure (resonator structure) of the compression mechanism unit 110 according to the second embodiment. FIG. 6 is a diagram corresponding to FIG. 5 of the first embodiment. Components similar to those in FIG. 5 are denoted by the same reference numerals, and description thereof is omitted. Also, in FIGS. 7 to 13 described in the following embodiments, the same reference numerals are given to the same components as those in FIG. 5 and the description thereof is omitted.

  As shown in FIG. 6, in the compression mechanism unit 110 according to the present embodiment, a constant volume of the resonance space 31 and a flow path 32 communicating with the resonance space 31 are formed in the lower bearing 10. The muffler structure communicates with the resonance space 31 through a flow path 32 communicating with the slit portion 15 through the suction hole 7a along the slit portion 15 of the inner peripheral surface opening portion 7e. The operations and effects of the present embodiment are the same as those described in the first embodiment.

Embodiment 3 FIG.
In the first and second embodiments described above, the configuration in which the resonance space 31 and the flow path 32 communicating with the resonance space 31 are formed in either the upper bearing 9 or the lower bearing 10 has been described. In the present embodiment, the case where the resonance space 31 and the flow path 32 communicating with the resonance space are formed in both the upper bearing 9 and the lower bearing 10 will be described.

  FIG. 7 is a partially enlarged longitudinal sectional view showing an example of a silencing structure (resonator structure) of the compression mechanism unit 110 according to the third embodiment. As shown in FIG. 7, the upper bearing 9 is formed with a constant volume of the resonance space 31a and a flow path 32a communicating with the resonance space 31a, and the lower bearing 10 is communicated with the fixed volume of the resonance space 31b and the resonance space 31b. A flow path 32b is formed. That is, the upper bearing 9 described in FIG. 5 and the lower bearing 10 described in FIG. 6 are combined. The operations and effects of the present embodiment are the same as those described in the first and second embodiments.

  Hereinafter, the term “resonator” refers to a silencing mechanism (a silencing structure) that includes the resonance space 31 and the flow path 32. As shown in FIG. 7, the compression mechanism unit 110 according to the present embodiment has the same volume of the resonance space 31 a of the upper bearing 9 and the volume of the resonance space 31 b of the lower bearing 10, and further the flow path 32 a of the upper bearing 9. The cross-sectional area and length are equal to the cross-sectional area and length of the flow path 32b of the lower bearing 10. As described above, the specific frequency band attenuated by the resonator is determined by the relationship between the volume of the resonance space 31, the length of the flow path 32 communicating with the resonance space 31, and the cross-sectional area. Therefore, according to the compression mechanism unit 110 according to the present embodiment, two equal resonators of the resonance space 31 of the upper bearing 9 and the resonance space 31 of the lower bearing 10 are provided. The silencing effect on the frequency band can be increased.

  FIG. 8 is a partially enlarged longitudinal sectional view showing an example of a silencing structure (resonator structure) of the compression mechanism unit 110 according to the third embodiment. FIG. 9 is a partially enlarged longitudinal sectional view showing an example of a silencing structure (resonator structure) of the compression mechanism unit 110 according to the third embodiment.

Hereinafter, the term “resonator” refers to a silencing mechanism including the resonance space 31 and the flow path 32.
8, the volume of the resonance space 31a of the upper bearing 9 and the volume of the resonance space 31b of the lower bearing 10 are different. Thereby, the frequency band attenuated by the resonator of the upper bearing 9 and the frequency band attenuated by the resonator of the lower bearing 10 become different frequency bands. With the structure shown in FIG. 8, even when there are two types of frequency bands to be attenuated, a silencing effect can be obtained for the two types of frequency bands.

  In the resonator of the compression mechanism section 110 shown in FIG. 9, the length of the flow path 32a of the upper bearing 9 and the length of the flow path 32b of the lower bearing 10 are different. Thereby, the frequency band attenuated by the resonator of the upper bearing 9 and the frequency band attenuated by the resonator of the lower bearing 10 become different frequency bands. With the structure shown in FIG. 9, even when there are two or more frequency bands to be attenuated, it is possible to obtain a silencing effect for the two frequency bands.

  As described above, the volume of the resonance space 31 may be changed, the length of the flow path 32 may be changed, and the cross-sectional area of the flow path 32 may be changed. The specific frequency band attenuated by the resonator is determined by the relationship between the volume of the resonance space 31, the length of the flow path 32 communicating with the resonance space 31, and the cross-sectional area, so that resonance occurs between the upper bearing 9 and the lower bearing 10. A desired frequency band can be attenuated by changing and combining the volume of the space 31, the length of the flow path 32, the cross-sectional area of the flow path 32, and the like.

Embodiment 4 FIG.
In the first and second embodiments, the resonance space 31 and the flow path 32 that communicates with the resonance space 31 are formed in the upper bearing 9 or the lower bearing 10. However, in the present embodiment, the flow that communicates with the resonance space 31. A mode in which the passage 32 is not provided and communicates directly from the suction hole 7a to the resonance space 31 formed in the upper bearing 9 or the lower bearing 10 through the slit portion 15 provided in the cylinder 7 will be described.

  FIG. 10 is a partially enlarged longitudinal sectional view showing an example of a silencing structure (resonator structure) of the compression mechanism unit 110 according to the fourth embodiment. As shown in FIG. 10, the resonance space 31 of the upper bearing 9 is formed at a position where a part of the resonance space 31 overlaps the slit portion 15. Thereby, the resonance space 31 and the slit part 15 communicate directly. The slit portion 15 is a flow path that allows the suction hole 7a and the resonance space 31 to communicate with each other.

  FIG. 11 is a partially enlarged longitudinal sectional view showing an example of a silencing structure (resonator structure) of the compression mechanism unit 110 according to the fourth embodiment. As shown in FIG. 11, the resonance space 31 of the lower bearing 10 is formed at a position where a part of the resonance space 31 overlaps the slit portion 15. Thereby, the resonance space 31 and the slit part 15 communicate directly. The slit portion 15 is a flow path that allows the suction hole 7a and the resonance space 31 to communicate with each other.

  The resonator of the compression mechanism 110 according to the present embodiment has a structure in which the slit portion 15 provided in the cylinder 7 is replaced with a function similar to the flow path 32 communicating with the resonance space 31 described in the first embodiment. It has become. By adjusting the dimensions of the slit portion 15 provided in the cylinder 7 and the overlap of the resonance space 31 provided in the slit portion 15 and the upper bearing 9, a specific pulsation generated in the suction refrigerant (refrigerant gas) is selected. An effect of attenuating the frequency band can be obtained.

  Further, compared to the process for forming the flow path 32 and the resonance space 31 in the upper bearing 9 or the lower bearing 10, only the process for forming the resonance space 31 is required, so that the processing cost can be reduced. .

Embodiment 5 FIG.
In the above-described fourth embodiment, the configuration in which the resonance space 31 is formed in either the upper bearing 9 or the lower bearing 10 has been described. In the present embodiment, a case will be described in which a resonance space 31 that directly communicates with the slit portion 15 is formed in both the upper bearing 9 and the lower bearing 10.

  FIG. 12 is a partially enlarged longitudinal sectional view showing an example of a silencing structure (resonator structure) of the compression mechanism unit 110 according to the fifth embodiment. As shown in FIG. 12, the upper bearing 9 is formed with a constant volume of resonance space 31a, and the lower bearing 10 is formed with a fixed volume of resonance space 31b. That is, the upper bearing 9 described in FIG. 10 and the lower bearing 10 described in FIG. 11 are combined. The operations and effects of the present embodiment are the same as those described in the fourth embodiment.

  As shown in FIG. 12, in the compression mechanism unit 110 according to the present embodiment, the volume of the resonance space 31 a of the upper bearing 9 and the volume of the resonance space 31 b of the lower bearing 10 are equal. As described above, the specific frequency band attenuated by the resonator is determined by the relationship between the volume of the resonance space 31, the length of the flow path 32 communicating with the resonance space 31, and the cross-sectional area. Therefore, according to the compression mechanism unit 110 according to the present embodiment, two equal resonators, that is, the resonance space 31a of the upper bearing 9 and the resonance space 31b of the lower bearing 10, are provided. The silencing effect on the frequency band can be increased.

  FIG. 13 is a partially enlarged longitudinal sectional view showing an example of a silencing structure (resonator structure) of the compression mechanism unit 110 according to the fifth embodiment.

  In the resonator of the compression mechanism 110 shown in FIG. 13, the volume of the resonance space 31 a of the upper bearing 9 is different from the volume of the resonance space 31 b of the lower bearing 10. Thereby, the frequency band attenuated by the resonator of the upper bearing 9 and the frequency band attenuated by the resonator of the lower bearing 10 become different frequency bands. With the structure shown in FIG. 13, even when there are two types of frequency bands to be attenuated, a silencing effect can be obtained for the two types of frequency bands.

  As described above, in the first to fifth embodiments, the slit portion 15 that has been vertically cut from the upper surface 7h to the lower surface 7i has been described. However, for example, the slit portion 15 cut out from the suction hole 7a to the upper surface 7h may be used. In this case, the resonance space 31 communicating with the suction hole 7 a is formed in the upper bearing 9.

  For example, the slit part 15 notched from the suction hole 7a to the lower surface 7i may be sufficient. In this case, the resonance space 31 that communicates with the suction hole 7 a is formed in the lower bearing 10. As described above, even when there is a slit only above or below the suction hole 7a, it is possible to expect a reduction in wear or the like due to contact between the vane 14 and the vane groove 7b.

  The rolling piston compressor according to the first to third embodiments forms a structure having an effect of attenuating the pulsation generated in the suction refrigerant gas inside the compression mechanism of the rotary compressor. In the rolling piston compressor according to the first to third embodiments, the upper bearing 9 and / or the lower bearing 10 which are components of the compression chamber 12 are provided with a resonance space 31 and a flow path 32 communicating with the resonance space 31 in a cylinder. 7 is formed through the slit portion 15 provided in FIG. Thereby, the resonance space 31 and the flow path 32 cause Helmholtz resonance and function as a silencer that attenuates the pulsation generated in the suction refrigerant gas in the same band as the resonance frequency. This silencer is formed on one of the upper bearing 9 and the lower bearing 10, or is formed on both the upper bearing 9 and the lower bearing 10, and the dimensions of the resonance space 31 and the flow path 32 communicating with the resonance space 31. Using a method of changing the relationship, it is possible to deal with any frequency band. Furthermore, the rolling piston compressor according to the first to third embodiments has the following characteristics.

  In a rolling piston compressor 100 having a compression mechanism unit 110 and a drive unit 120 in the casing 2 and having a high operating pressure represented by carbon dioxide, the refrigerant used is a component of the compression mechanism unit 110. A certain cylinder 7 has a suction hole 7a for sucking a refrigerant from the outside of the casing 2 through a suction pipe 19, and the cylinder 7 separates the internal compression chamber 12 into a low pressure chamber 12a and a high pressure chamber 12b. 14 is formed, and when a compressive load P is applied to the vane 14 on the high pressure side of the vane 14, the vane 14 presses the vane groove 7 b on the cylinder 7. A slit portion 15 that forms a partition wall 16 between the vane groove 7b is provided so as to penetrate the cylinder 7 in the vertical direction, and is compressed into the vane 14. When the weight P is applied, the partition 16 includes a mechanism that elastically bends in the pressing direction of the vane 14, and the cylinder 7 of the eccentric shaft (crankshaft 5) that transmits the drive from the drive unit 120. The two bearings (upper bearing 9 and lower bearing 10) positioned above and below between have a flange portion, and the upper bearing 9 and / or the lower bearing 10 flange portion through the slit portion 15 through the suction hole 7a. A resonance space 31 for attenuating the pulsation frequency of the refrigerant sucked into the cylinder internal compression chamber 12 and a flow path 32 communicating with the resonance space 31 are provided.

  In the rolling piston compressor according to the first to third embodiments, the resonance space 31 is formed in the flange portion of the upper bearing 9 and / or the lower bearing 10, and the flow path 32 communicates with the resonance space 31. Is characterized by communicating with the slit portion 15 (substituting the slit portion 15).

  According to the rolling piston compressor 100 according to the first to fifth embodiments, the upper bearing 9 and / or the lower bearing 10 are provided with the resonance space 31 and the flow path 32 communicating with the resonance space (or only the resonance space 31). Therefore, there are fewer restrictions on the shape and the size than when the cylinder 7 is provided with the resonance space 31 and / or the flow path 32 (or only the resonance space 31) communicating with the resonance space.

  Further, according to the rolling piston compressor 100 according to the first to fifth embodiments, the resonance space 31 and the flow path 32 (or only the resonance space 31) communicating with the resonance space can be formed with a simple shape. When the upper bearing 9 is a cast product, machining is performed by forming a resonance space 31 and a flow path 32 (or only the resonance space 31) communicating with the resonance space in advance in the mold from the time of molding. The sound deadening structure can be obtained without

  As mentioned above, although Embodiment 1-5 was demonstrated, you may implement combining 2 or more embodiment among these. Alternatively, one of these embodiments may be partially implemented. Or you may implement combining two or more embodiment among these partially.

  2 Casing, 4 Electric motor, 4a Stator, 4b Rotor, 5 Crankshaft, 5a Eccentric part, 7 Cylinder, 7a Suction hole, 7b Vane groove, 7c Discharge port, 7d Vane groove hole, 7e Inner peripheral surface opening, 7f Inside Peripheral surface, 7g outer peripheral surface, 7h upper surface, 7i lower surface, 8 rolling piston, 9 upper bearing, 10 lower bearing, 12 compression chamber, 12a low pressure chamber, 12b high pressure chamber, 14 vane, 15 slit portion, 16 partition, 19 suction pipe , 20 Discharge pipe, 22 Lubricating oil, 31, 31a, 31b Resonance space, 32, 32a, 32b Flow path, 40 Recessed part, 100 Rolling piston type compressor, 110 Compression mechanism part, 120 Drive part.

Claims (3)

In a rolling piston compressor having a compression mechanism for sucking and compressing refrigerant,
The compression mechanism is
A cylinder having an upper surface, a lower surface, an inner peripheral surface, and an outer peripheral surface, the cylinder having a suction hole that penetrates from the outer peripheral surface to the inner peripheral surface and sucks the refrigerant into the interior;
The cylinder is
It said inner peripheral surface a said notch is formed by cutting up the lower surface from the upper surface, shorter than the diameter of the circumferential direction of the inner peripheral surface opening of the circumferential direction of the notch width is the suction hole, wherein Having a notch formed by notching from the upper surface to the lower surface within the range of the circumferential diameter of the inner circumferential surface opening,
The rolling piston compressor further includes:
A rolling piston that compresses the refrigerant sucked from the suction hole by rotating eccentrically along the inner peripheral surface;
A crankshaft coupled to the rolling piston and transmitting rotational force to the rolling piston by rotating;
An upper bearing that supports the crankshaft and closes an upper surface of the cylinder;
A lower bearing for supporting the crankshaft and closing the lower surface of the cylinder;
At least one of the upper bearing and the lower bearing has a space that communicates with the notch.
A rolling piston compressor characterized by that.   2. The rolling piston compressor according to claim 1, wherein a depth width of the notch portion is equal to or longer than a notch width in the circumferential direction. At least one of the upper bearing and the lower bearing is the space portion,
A resonant space that attenuates the pulsation frequency generated from the refrigerant sucked from the suction hole;
Rolling piston type compressor according to claim 1 or 2, characterized in that it comprises a channel section which communicates with the resonance space portion and the notch.

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