CN100458165C - Rotary compressor - Google Patents

Abstract

Disclosed is a rotary compressor capable of inhibiting the pressure fluctuation generated in the ejection space of the intermediate container to improve energy efficiency. The rotary compressor(1)comprises a rotary type low pressure side compressing part(10)compressing the refrigerant; a rotary type high pressure side compressing part(12)compressing the refrigerant at opposite phase with respect to the compressing procedure of the low pressure side compressing part; and an intermediate container(18)connected between the refrigerant ejection opening(14)of the low pressure side compressing part and the refrigerant suction opening(16)of the high pressure side compressing part. The interior ejection space(20)of the intermediate container is divided into two parts, that is a main stream side space(20a)and an opposite main stream side space(20b), by an isolating part(22). The refrigerant ejection opening of the low pressure side compressing part and the refrigerant suction opening of the high pressure side compressing part are communicated with each other at the main stream side space, and a refrigerant flow path(20c)connecting the main stream side space with the opposite main stream side space is formed at the isolating part.

Description

rotary compressor

technical field

The present invention relates to a rotary compressor suitable for use in refrigeration cycle devices such as air conditioners for raising and lowering the temperature of indoor air.

Background technique

A refrigerating cycle device typified by an air conditioner raises or lowers the temperature of air or water using a refrigerating cycle in which a refrigerant is repeatedly vaporized and liquefied. A two-stage rotary compressor having a two-stage compression mechanism for compressing refrigerant in stages is known as a refrigerant compressor suitable for this refrigeration system. For example, a rotary two-stage compressor has: a rotary low-pressure side compression section that compresses refrigerant; a rotary high-pressure side compression section that compresses refrigerant in an opposite phase to the compression process of the low-pressure side compression section; An intermediate container of an internal space (hereinafter referred to as a discharge space) in which the refrigerant discharge port of the side compression unit communicates with the refrigerant suction port of the high-pressure side compression unit.

In the intermediate vessel of such a rotary two-stage compressor, pressure fluctuations occur in the discharge space due to a phase difference (for example, 180 degrees) between the discharge process of the low-pressure side compressor and the suction process of the high-pressure side compressor. That is, a pressure increase due to a state in which the refrigerant discharged into the discharge space cannot be sucked and a pressure decrease due to a state in which suction starts before the refrigerant is discharged into the discharge space are repeated.

Therefore, in order to reduce the pressure fluctuation generated in the discharge space, the volume of the discharge space is enlarged as much as possible. For example, it has been proposed to make the inner peripheral wall of the intermediate container concave and convex in the radial direction to form a petal shape, thereby avoiding the connection member attached to the peripheral wall of the intermediate container, while ensuring the volume of the discharge space as much as possible, and suppressing the discharge. Overcompression loss in space (for example, Patent Document 1).

Patent Document 1: Japanese Unexamined Patent Publication No. 2003-166472 (page 10, FIG. 10 )

However, since the discharge space of the intermediate container is a uniformly enlarged space without a shield, if the refrigerant is discharged into the discharge space, the pulsation component may resonate without attenuation at a specific number of revolutions. There are cases where pressure fluctuations in the discharge space increase. Especially when the specific operating speed of the compressor is high, the pressure fluctuation may further increase. If the pressure fluctuation increases, the kinetic energy due to the pressure fluctuation will be dissipated as frictional heat on the refrigerant flow path wall, and the energy loss will increase, which will cause a decrease in the coefficient of performance (COP) of the refrigeration cycle. Conventional technologies such as Patent Document 1 do not consider such pressure fluctuations, and there is room for improvement in the energy efficiency of the rotary compressor.

Contents of the invention

An object of the present invention is to realize a rotary compressor more suitable for suppressing pressure fluctuations generated in a discharge space of an intermediate container and improving energy efficiency.

In order to solve the above-mentioned problems, the rotary compressor of the present invention is characterized in that,

include:

Rotary low-pressure side compression part, which compresses the refrigerant;

a rotary high-pressure side compression section that compresses the refrigerant in anti-phase with respect to the compression process of the low-pressure side compression section; and

an intermediate container communicating with the refrigerant discharge port of the low-pressure side compression unit and the refrigerant suction port of the high-pressure side compression unit,

The inner space of the intermediate container is divided into at least two spaces by a partition member, and the refrigerant discharge port of the low-pressure side compression part and the refrigerant suction port of the high-pressure side compression part are connected in one space, and the partition The component forms a refrigerant flow path connecting the two spaces.

In this case, the intermediate container may be formed to have: a disc-shaped end plate portion; an outer wall portion that rises from the peripheral portion of the end plate portion in the axial direction to define the circumferential direction of the discharge space; A sub-bearing standing upright in the axial direction at the center of the end plate portion; and a closing plate facing the end plate portion and closing the opening on the front end side of the outer wall portion. The spacer here is a beam erected from the sub-bearing on the outer peripheral wall and erected on the plate surface of the end plate. A refrigerant flow path is formed between them.

That is, the space where the refrigerant discharge port of the low-pressure side compression unit communicates with the refrigerant suction port of the high-pressure side compression unit serves as the main flow side space through which the main flow of the refrigerant flows. In addition, another space communicated with the main flow side space via the partition member serves as an anti-main flow side space into which the pulsation component of the refrigerant flows in and out.

Thus, when the refrigerant is discharged from the low-pressure side compression unit to the intermediate tank, the main flow of the refrigerant is sucked into the high-pressure side compression unit after flowing through the main flow side space, but a part of the pulsation component of the refrigerant in this process or All, flow in and out of the space on the counter-mainstream side. That is, the anti-mainstream side space functions as a so-called cavitated resonator, ie, a buffer, which prevents resonance of the pulsation component of the refrigerant. Accordingly, since the resonance of the pulsation component in the discharge space is suppressed, the pressure fluctuation generated in the discharge space is suppressed. As a result, energy loss due to pressure fluctuations can be reduced and energy efficiency can be improved.

In addition, it is preferable that the sub-bearing is formed by an enlarged diameter portion whose outer diameter on the end plate side is larger than that on the front end side, and that the axial dimension of the spacer from the end plate portion is smaller than the enlarged diameter portion.

In addition, the spacer member is formed on the front end side: a parallel portion parallel to the plate surface of the end plate portion; an inner peripheral tapered portion inclined toward the sub-bearing side from the inner peripheral edge of the parallel portion toward the axial direction; and From the inner peripheral edge of the parallel portion toward the axial direction, the outer peripheral side taper portion inclined toward the outer wall portion side, the refrigerant flow path can be formed to be divided by the parallel portion, the inner peripheral side taper portion, the outer peripheral side taper portion, and the closing plate. Openings with trapezoidal cross-section. That is, the opening width of the refrigerant channel can be changed to a certain width such as gradually increasing the opening width toward the axial direction. In other words, by adjusting the inclination angle of the inner tapered portion or the outer tapered portion, the size of the cross-sectional area of the refrigerant flow path can be finely adjusted. Therefore, the pressure fluctuation can be reduced over a wide range of operating revolutions without being limited to a specific operating revolution.

In addition, in the intermediate container, a reinforcement beam erected on the plate surface of the end plate portion from the sub-bearing to the outer peripheral wall may be installed in the other space partitioned by the spacer. Here, the reinforcing beam is formed so that the dimension in the axial direction from the end plate portion is smaller than that of the spacer member. Thereby, the rigidity of the intermediate container can be increased, so that deformation due to a pressure load or a load of the connecting elements at the time of assembly can be suppressed.

According to the present invention, it is possible to realize a rotary compressor more suitable for suppressing pressure fluctuations generated in the discharge space of the intermediate container and improving energy efficiency.

Description of drawings

FIG. 1 is a longitudinal sectional view showing the structure of a rotary compressor to which one embodiment of the present invention is applied;

Fig. 2 is a diagram showing a low-pressure side compression section and a high-pressure side compression section of Fig. 1;

Fig. 3 is a bottom view of the intermediate container of Fig. 1 viewed from the lower side;

Fig. 4 is the A-A sectional view of the intermediate container of Fig. 3;

Fig. 5 is a diagram showing the flow of refrigerant in the discharge space of the intermediate container of Fig. 1;

Fig. 6 is a graph showing a comparison of the pressure amplitude of the intermediate vessel of Fig. 1 with the prior art;

Fig. 7 is the B-B sectional view of the intermediate container of Fig. 3;

Fig. 8 is a C-C sectional view of the intermediate container of Fig. 3;

Fig. 9 is a D-D sectional view of the intermediate container of Fig. 3;

Figure 10 is a top view of the cover of Figure 1 or Figure 4;

Fig. 11 is a sectional view of the elastomer of Fig. 1 or Fig. 4;

Fig. 12 is a graph showing the measurement results of the rate of change of the refrigeration cycle coefficient of performance (COP) of the air conditioner to which the embodiment of the present invention is applied;

Fig. 13 is a sectional view showing another first example of the intermediate container to which the present invention is applied;

Fig. 14 is a sectional view showing another second example of the intermediate container to which the present invention is applied.

In the picture:

1-rotary compressor; 10-low-pressure side compression part; 12-high-pressure side compression part; 14-refrigerant injection port; 16-refrigerant suction port; 18-intermediate container; 20-spray space; 20a-mainstream side space ; 20b-space on the side of the anti-main flow; 20c-refrigerant flow path; 22-isolating components.

Detailed ways

One embodiment of a rotary compressor to which the present invention is applied will be described with reference to the drawings. FIG. 1 is a longitudinal sectional view showing the structure of a rotary compressor according to this embodiment. FIG. 2 is a diagram showing a low-pressure side compression unit and a high-pressure side compression unit in FIG. 1 . Fig. 3 is a bottom view of the intermediate container of Fig. 1 viewed from the lower side. Fig. 4 is an A-A sectional view of the intermediate container of Fig. 3 .

As shown in FIG. 1 , a rotary compressor 1 applied to a refrigeration cycle apparatus such as an air conditioner has a two-stage compression mechanism for compressing refrigerant in stages. More specifically, the rotary compressor 1 has: a rotary low-pressure side compressor 10 that compresses a refrigerant (for example, R410A); side compression unit 12 ; and intermediate tank 18 having an internal space 20 (hereinafter referred to as discharge space 20 ) communicating with refrigerant discharge port 14 of low-pressure side compression unit 10 and refrigerant suction port 16 of high-pressure side compression unit 12 .

Here, applying to the intermediate container 18 of the rotary compressor 1, as shown in FIGS. And, the refrigerant discharge port 14 of the low-pressure side compression part 10 and the refrigerant suction port 16 of the high-pressure side compression part 12 are communicated in one space 20a (hereinafter referred to as the main flow side space 20a), and the partition member 22 forms a connecting main flow side space. 20a and the other space 20b (hereinafter referred to as the counter main flow side space 20b ) of the refrigerant flow path 20c.

That is, the intermediate tank 18 has: the main flow side space 20a communicating with the refrigerant discharge port 14 of the low pressure side compression part 10 and the refrigerant suction port 16 of the high pressure side compression part 12; The space 20b on the counter main flow side, where the isolation member 22 forms an opening that communicates the space 20a on the main flow side and the space 20b on the counter main flow side, that is, a refrigerant flow path 20c. Accordingly, since the anti-main flow side space 20b functions as a so-called cavitated resonator, ie, a buffer, which prevents resonance of the pulsation component of the refrigerant, pressure fluctuations in the discharge space 20 can be suppressed and energy efficiency can be improved.

The rotary compressor 1 of this embodiment will be described in further detail. As shown in FIG. 1 , the rotary compressor 1 houses a motor 24 , an end plate portion 38 , a high-pressure side compressor 12 , an intermediate partition plate 13 , a low-pressure side compressor 10 , and an intermediate container 18 in an airtight container 26 . Specifically, the airtight container 26 is divided into an airtight space 39 in which the motor 24 is disposed, and a space for rotating compression elements such as the low-pressure side compression unit 10 and the high-pressure side compression unit 12 , via the end plate portion 38 . On the side of the rotating compression element, the high-pressure side compression part 12, the intermediate partition plate 13, the low-pressure side compression part 10, and the intermediate container 18 are stacked in the axial direction from the motor 24 side and integrally fixed by the connecting element 15 (such as a bolt).

The airtight container 26 has: a cylindrical body part 28; a substantially bowl-shaped cover part 29 for closing the opening of the body part 28 on the motor 24 side; 30. The cover portion 29 is provided with a discharge pipe 31 that discharges refrigerant compressed to a high pressure Pd. In addition, for convenience of description, the axial direction of the trunk|drum 28 is suitably called a vertical direction, and the horizontal direction orthogonal to an axial direction is suitably called a horizontal direction. In addition, the direction from the body part 28 to the cover part 29 side in the axial direction is suitably called an upper side, and the direction from the body part 28 to the bottom part 30 side in an axial direction is suitably called a down side.

The motor 24 is disposed in a closed space 39 partitioned by an end plate portion 38 on the upper side in the closed container 26 . The electric motor 24 has: a stator 32 as a stator installed in a ring shape along the inner peripheral surface of the airtight container 26; a rotor 34 as a rotor inserted into the inner side of the stator 32 with a gap; Attached to the rotating shaft 36 of the rotor 34 . The rotating shaft 36 is provided with two eccentric portions, that is, an eccentric portion 42 for high compression and an eccentric portion 44 for low compression, at a portion on the front end side. Here, the eccentric portion 42 is provided at a position shifted upward in the axial direction from the eccentric portion 44 , and its eccentric direction is opposite to that of the eccentric portion 44 , that is, the phase difference is, for example, 180 degrees.

The end plate portion 38 is an annular plate member fixed by welding or the like along the inner peripheral surface of the airtight container 26 . The end plate portion 38 is formed at the center of the cylindrical main bearing 40 that pivotally supports the rotary shaft 36 to rise upward. In addition, the end plate portion 38 is formed with a discharge port 46 penetrating in the thickness direction. A discharge valve 48 is arranged at the discharge port 46 . In addition, the end plate portion 38 is provided with a discharge cap 50 at the center of the upper end surface. The discharge cap 50 is a hollow annular member surrounding the rotating shaft 36 , and its internal space communicates with the discharge port 46 . In addition, a discharge port 51 is formed in a portion of the discharge cover 50 on the motor 24 side.

The high-pressure-side compression section 12 is arranged between the end plate section 38 and the intermediate partition plate 13 . The high-pressure side compression unit 12, as shown in FIGS. 1 and 2 , has: a substantially cylindrical cylinder 52 having a portion having the same outer diameter as the inner diameter of the airtight container 26; a cylindrical roller 54 in which Fitting to the outer periphery of the eccentric portion 42 located in the cylinder 52; the wing 56, the front end of which abuts against the outer peripheral surface of the roller 54, and is supported on the cylinder 52 by an elastic force applying mechanism (such as a coil spring) so as to be able to move forward and backward; and the refrigerant suction The port 16 penetrates in the radial direction and communicates with the inside of the cylinder 52 . Here, the cylinder 52 is sandwiched between the lower end surface of the end plate portion 38 and the upper end surface of the intermediate partition plate 13 to close the internal space 58 . In addition, the blade 56 moves forward and backward while being in contact with the outer peripheral surface of the roller 54 that rotates in conjunction with the eccentric movement of the eccentric portion 42, thereby dividing the internal space 58 of the cylinder 52 into a refrigerant compression chamber and a refrigerant compression chamber. suction chamber. Further, the refrigerant suction chamber communicates with the discharge space 20 of the intermediate tank 18 via the intermediate flow path 60 connected to the refrigerant suction port 16 . In addition, the refrigerant compression chamber communicates with the sealed space 39 through the discharge port 46 formed in the end plate portion 38 .

The intermediate partition plate 13 is a blocking plate sandwiched between the high-pressure side compression portion 12 and the low-pressure side compression portion 10 . The intermediate partition plate 13 has a through hole formed in the center through which the rotation shaft 36 is inserted. The axis of the through hole is substantially coincident with the rotation axis.

The low-pressure side compression unit 10 is arranged between the intermediate partition plate 13 and the intermediate container 18 . The low-pressure side compression unit 10, as shown in FIGS. 1 and 2 , has: a substantially cylindrical cylinder 62 having a portion having the same outer diameter as the inner diameter of the airtight container 26; a cylindrical roller 64 in which Fitted to the outer periphery of the eccentric portion 44 located in the cylinder 62; the wing 66, the front end of which abuts against the outer peripheral surface of the roller 64, and is supported by the elastic force applying mechanism (for example, a coil spring) on the cylinder 62 so as to be able to move forward and backward; and the refrigerant suction The port 70 penetrates in the radial direction and communicates with the inside of the cylinder 62 . Here, the cylinder 62 is sandwiched between the lower end surface of the intermediate partition plate 13 and the upper end surface of the intermediate container 18 to block the internal space 71 . Furthermore, the blade 66 moves forward and backward while being in contact with the outer peripheral surface of the roller 64 that rotates in conjunction with the eccentric movement of the eccentric portion 44, thereby dividing the internal space 71 of the cylinder 62 into a refrigerant compression chamber and a refrigerant compression chamber. suction chamber. Into the refrigerant suction chamber, gas refrigerant discharged from equipment of the refrigeration cycle apparatus (for example, a refrigerant evaporator) flows in through a refrigerant pipe 72 connected to the refrigerant suction port 70 . The refrigerant compression chamber communicates with the intermediate container 18 .

The intermediate container 18 is a cylindrical container that temporarily stores the refrigerant discharged from the low-pressure side compressor 10 . More specifically, as shown in FIG. 1 , the intermediate container 18 is a concave container, which has: a disc-shaped end plate portion 74 in contact with the lower end surface of the low-pressure side compression portion 10; The cylindrical sub-bearing 43 formed to stand upright in the center; the outer wall portion 78 protruding downward from the peripheral portion of the end plate portion 74 to distinguish the circumferential direction of the discharge space 20; and the outer wall portion 78 penetrating in the horizontal direction. Refrigerant outlet 79. That is, the intermediate container 18 is a concave container that opens in the opposite direction with respect to the low-pressure side compression unit 10 side. In addition, the end plate portion 74 is formed to penetrate in the thickness direction with the refrigerant discharge port 14 communicating with the refrigerant compression chamber of the low-pressure side compression portion 10 . The refrigerant discharge port 14 is provided with a discharge valve 80 . In addition, the refrigerant discharge port 79 is provided with an intermediate flow path 60 that communicates the discharge space 20 with the refrigerant suction chamber of the high-pressure side compression unit 12 . Such an intermediate container 18 is provided with a cover 82 which is an annular plate closing plate that closes the opening on the lower end surface.

The basic operation of the rotary compressor 1 configured in this way will be described. Arrows in FIG. 1 indicate the flow of gas refrigerant as a working fluid. Low-pressure Ps gas refrigerant discharged from equipment of the refrigeration cycle apparatus (for example, a refrigerant evaporator) is sucked into the cylinder 62 of the low-pressure side compressor 10 through the refrigerant pipe 72 . The attracted gas refrigerant is compressed in the refrigerant compression chamber of the cylinder 62 by the eccentric rotation of the roller 64 . When the pressure of the refrigerant compression chamber reaches a predetermined intermediate pressure Pm, the gas refrigerant in the refrigerant compression chamber passes through the opening of the discharge valve 80 and is discharged into the discharge space 20 through the refrigerant discharge port 14 . Here, the discharge space 20 is a space isolated from the space in the intermediate container 18 , that is, the space isolated from the closed space 39 in the airtight container 26 , so its internal pressure is basically the intermediate pressure Pm.

The gas refrigerant discharged into the discharge space 20 is sucked from the refrigerant suction port 16 into the cylinder 52 of the high-pressure side compression unit 12 via the intermediate flow path 60 . The attracted gas refrigerant is compressed in the refrigerant compression chamber of the cylinder 52 by the eccentric rotation of the roller 54 . When the pressure of the refrigerant compression chamber reaches a predetermined high pressure Pd, the gas refrigerant in the refrigerant compression chamber passes through the opening of the discharge valve 48 and is discharged from the discharge port 46 . The discharged gas refrigerant flows out into the sealed space 39 through the discharge port 51 of the discharge cover 50 . The gas refrigerant that has flowed out flows through the gap of the motor 24, and is then discharged from the discharge pipe 31 to equipment of the refrigeration cycle apparatus (for example, a refrigerant condenser).

In the stepwise compression process of the refrigerant, in the present embodiment, the intermediate container 18 is provided with the anti-mainstream side space 20b having a hollow resonance function, thereby reducing the discharge process and the flow caused by the low-pressure side compression part 10. The pressure fluctuation in the discharge space 20 is caused by the phase difference in the suction process of the high-pressure side compressor 12 . In addition, the pressure fluctuation is related to the speed of sound of the refrigerant and the refrigerant discharge amount of the low-pressure side compressor 10, especially the operating speed of the rotary compressor 1 and the volume of the discharge space 20. The sonic velocity of the refrigerant is closely related to the resonance of the refrigerant pulsation component.

Here, the intermediate container 18 will be described in further detail with reference to FIGS. 2 to 4 . As shown in FIG. 2 , the discharge space 20 of the intermediate container 18 is divided by a partition member 22 into a main flow side space 20 a and an anti main flow side space 20 b. The partition member 22 is formed with a refrigerant flow path 20c which is an opening communicating with the main flow side space 20a and the counter main flow side space 20b. That is, the discharge space 20 is divided into a main flow side space 20a through which the refrigerant mainly flows, and a counter main flow side space 20b through which the time-varying component of the refrigerant mainly flows, bounded by the refrigerant passage 20c. Furthermore, the main flow side space 20 a communicates with the counter main flow side space 20 b across the partition member 22 . Here, the space 20b on the reverse main flow side functions as a hollow resonator because the refrigerant enters and exits through the refrigerant flow path 20c.

More specifically, the intermediate container 18 is a cast member or an iron-based sintered member. As shown in FIGS. 3 and 4 , the end plate portion 74 , the outer wall portion 78 , and the sub-bearing 43 are integrally formed. That is, the intermediate container 18 is formed in a generally concave shape with one end surface opened on the lid 82 side.

The end plate portion 74 is a circular plate formed with a seat 84 for installing the refrigerant discharge port 14 and the discharge valve 80 of the low-pressure side compression unit 10 . In addition, the outer wall portion 78 is formed in a substantially cylindrical shape, and defines the circumferential direction of the discharge space 20 . In the outer wall portion 78 , a contact surface 81 formed parallel to the plate surface of the end plate portion 74 is in contact with a cover 82 . In addition, the contact surface 81 is formed by molding, cutting, or grinding. In addition, the outer wall portion 78 is formed with a plurality of (for example, four) holes 86 for the connecting elements 15 penetrating in the axial direction. These plural holes 86 are formed at equal intervals on the same circumference. In addition, the outer wall portion 78 is formed in a petal shape in which the inner peripheral wall is concave-convex in the radial direction. More specifically, in the inner peripheral wall of the outer wall portion 78, the portion where the hole 86 is arranged is concavely formed radially inward, and the portion between one hole 86 and the other adjacent hole 86 is formed convexly radially outward. . By forming the inner peripheral wall of the outer wall portion 78 in a petaloid shape in this way, the volume of the discharge space 20 can be ensured while avoiding the holes 86 as much as possible. In addition, the volume of the discharge space 20 here is larger than the refrigerant discharge amount of the low-pressure side compression unit 10 . Therefore, when the refrigerant is discharged from the low-pressure side compressor 10 to the discharge space 20 , overcompression loss in the discharge space 20 can be suppressed.

The sub-bearing 43 is formed to rise in a substantially cylindrical shape at the center of the end plate portion 74 . The sub-bearing 43 has a stepped portion formed on the surface on the outer diameter side, that is, the outer peripheral wall. That is, the sub-bearing 43 is formed by an enlarged diameter portion whose outer diameter on the side of the end plate portion 74 is larger than that on the side of the cover 82 . The stepped portion has a flat surface 88 opposite to the flat surface of the cover 82 . The flat surface 88 is a concave portion whose height is smaller than the contact surface 81 of the outer wall portion 78 . An elastic body 90 is interposed in a gap formed between the flat surface 88 and the cover 82 . In addition, the height referred to in this embodiment is a dimension in the axial direction based on the end plate portion 74 .

In addition, in the sub-bearing 43 , the inner diameter on the side of the end plate portion 74 is smaller than the inner diameter on the side of the cover 82 , so that a stepped portion is formed. That is, in the sub-bearing 43 , a contact portion 92 that pivotally supports the rotary shaft 36 is formed on the end plate portion 74 side, and a non-contact portion 94 that does not pivotally support the rotary shaft 36 is formed on the cover 82 side. Here, the flat surface 88 formed on the outer peripheral wall of the sub-bearing 43 is located on the outer peripheral portion of the non-contact portion 94 . Thereby, since the pressure load or clamp load from the cover 82 or the elastic body 90 is absorbed by the non-contact portion 94 , the frictional force between the sub-bearing 43 and the rotary shaft 36 can be reduced. In addition, the flat surface 88 is integrally formed as a part of the intermediate container 18, but may be formed by machining such as cutting.

Furthermore, the intermediate container 18 of this embodiment is formed with a partition member 22 that divides the discharge space 20 into a main flow side space 20a and a counter main flow side space 20b, as shown in FIGS. 3 and 4 . The spacer member 22 is, as shown in FIG. 3 , a beam that is erected on the lower end surface of the end plate portion 74 by spanning the outer peripheral wall 78 in the radial direction from the sub-bearing 43 . That is, the spacer member 22 is a barrier plate with a substantially rectangular cross section that connects the outer wall of the sub-bearing 43 and the inner wall of the outer wall portion 78 . In this embodiment, two beams are formed on a straight line connecting the center of the sub-bearing 43 and the center of the connecting hole 86 , but two or more beams may be formed radially from the sub-bearing 43 . In short, what is necessary is just to divide the discharge space 20 into the main flow side space 20a and the counter main flow side space 20b by two or more beams.

As shown in FIG. 4 , such a spacer 22 forms a refrigerant flow path 20 c with a substantially trapezoidal opening cross-section between the cover 82 . More specifically, the spacer 22 is formed on the front end side with a parallel portion 22a whose height M is smaller than the contact surface 81 of the outer wall portion 78 and parallel to the lower end surface of the end plate portion 74; The outer peripheral tapered portion 22c is inclined toward the outer wall portion 78 from the outer peripheral edge of the parallel portion 22a toward the axial direction. Here, the inner peripheral tapered portion 22 b is an inclined surface connecting the inner peripheral edge of the parallel portion 22 a and the outer peripheral edge of the flat surface 88 . In addition, the outer peripheral side tapered portion 22c is an inclined surface connecting the outer peripheral edge of the parallel portion 22a to the inner peripheral edge of the outer wall portion 78 . That is, the space partitioned by the parallel part 22a, the inner peripheral taper part 22b, the outer peripheral taper part 22c, and the cover 82 becomes the refrigerant|coolant flow path 20c. In addition, although the inclination angle of the inner peripheral side taper part 22b and the outer peripheral side taper part 22c here is 45 degrees with respect to the rotating shaft 36, for example, it can be changed as needed. That is, to adjust the channel cross-sectional area S of the refrigerant channel 20c, it is only necessary to change the height of the parallel portion 22a or the inclination angles of the inner tapered portion 22b and the outer tapered portion 22c.

FIG. 5 is a diagram showing the flow of refrigerant in the discharge space 20 of the intermediate container 18 in FIG. 1 . As shown in FIG. 5 , when the gas refrigerant is discharged from the low-pressure side compression unit 10 to the intermediate container 18 through the refrigerant discharge port 14 , the main flow of the refrigerant passes through the main flow side space 20 a and then passes through the refrigerant discharge port 79 . While being sucked into the high-pressure side compression unit 12, part or all of the pulsating component of the refrigerant, that is, the refrigerant fluctuation component, flows into and out of the anti-mainstream side space 20b. That is, the anti-mainstream side space 20b functions as a so-called hollow resonator, ie, a buffer, which prevents resonance of the pulsation component of the refrigerant. Accordingly, since the resonance of the pulsation component in the discharge space 20 is suppressed, an increase in the pressure fluctuation generated in the discharge space 20 is suppressed. As a result, energy loss due to pressure fluctuations can be reduced, and energy efficiency can be improved.

In short, since the discharge space 20 has the anti-mainstream side space 20b bounded by the refrigerant flow path 20c and functioning as a hollow resonator, the pressure fluctuation of the intermediate pressure Pm generated in the discharge space 20 is suppressed.

FIG. 6 is a graph comparing the pressure amplitude of the intermediate container 18 according to the present embodiment with that of the prior art. 6 represents the operating revolutions (min ⁻¹ ) of the rotary compressor 1 , and the vertical axis represents the pressure amplitude (MPa) of the intermediate vessel 18 against the operating revolutions. As shown in FIG. 6, as the operating revolution number increases from the lowest revolution number, the pressure amplitude increases. In addition, in the prior art, the pressure amplitude becomes extremely large in the range of operating revolutions, for example, 4000 (min ⁻¹ ) to 6000 (min ⁻¹ ). That is, since the range of general operating revolutions is, for example, 1000 (min ⁻¹ ) to 8000 (min ⁻¹ ), it can be seen that the pressure amplitude relatively increases on the high revolution side in the conventional art. In this regard, according to the present embodiment, since the maximum value of the pressure amplitude on the high rotation side can be reduced, the coefficient of performance (COP) of the refrigeration cycle can be improved, and noise and vibration generated in the rotary compressor 1 can be suppressed.

In addition, according to the present embodiment, since the opening width of the refrigerant passage 20c is gradually increased toward the axial direction, the opening width is changed at a certain width, so it is not limited to a certain number of operating revolutions (frequency ) and can reduce pressure fluctuations in a wide range of operating revolutions. More specifically, in the intermediate container 18 of this embodiment, by changing the height N of the parallel portion 22a of the partition member 22, or by changing the inclination angles of the inner tapered portion 22b and the outer tapered portion 22c, it is possible to finely adjust the cooling effect. The size of the channel cross-sectional area S of the agent channel 20c. For example, if the cross-sectional area S of the flow path is reduced, the resonance function of the space 20b on the anti-mainstream side will be exhibited in the range on the high rotation side. In addition, if the cross-sectional area S of the flow passage is increased, the resonance function of the space 20b on the anti-mainstream side will be exhibited in the range on the low rotation side. However, if the flow channel cross-sectional area S is excessively increased, the discharge space 20 is substantially the same as a conventional space that is enlarged in the same way, and therefore the resonance function may not be exhibited, and pressure fluctuations may not be sufficiently suppressed. Therefore, the size of the cross-sectional area S of the flow path is preferably formed to be equal to or larger than a predetermined area. An appropriate value of the channel cross-sectional area S can be obtained by actual measurement, for example.

In addition, in the intermediate container 18 of the present embodiment, as shown in FIGS. 3 and 4 , the second beam 96 as a reinforcing member is provided in the space 20b on the reverse main flow side. The beam 96 is similar to the spacer member 22 in that it extends from the sub-bearing 43 to the outer peripheral wall 78 in the radial direction and is integrally formed on the lower end surface of the end plate portion 74, but has a height L ratio of the spacer member 22. The point that the height N of the parallel surface 22a is small is different. By providing such a beam 96, since the rigidity of the intermediate container 18 can be increased, deformation due to a pressure load or a load of the connecting element 15 at the time of assembly can be suppressed.

Further, the intermediate container 18 will be described. Fig. 7 is a B-B sectional view of the intermediate container in Fig. 3 . This FIG. 7 is a diagram showing the form of the spacer 22 in the B-B cross section. As shown in FIG. 7 , the spacer member 22 is formed such that the base portion expands downward toward the end plate portion 74 . That is, in the spacer member 22, the leg part 98 as a reinforcement member is formed in the joint part with the end plate part 74. As shown in FIG. Accordingly, even when the friction loss is reduced by reducing the thickness of the spacer 22 , that is, the flow path length of the refrigerant flow path 20 c , the rigidity of the spacer 22 can be ensured.

Fig. 8 is a C-C sectional view of the intermediate container of Fig. 3 . This FIG. 8 is a diagram showing the form of the beam 96 in the C-C section. As shown in FIG. 8 , the beam 96 is formed so that the base portion expands downward toward the end plate portion 74 . That is, the beam 96 has the leg part 100 as a reinforcement member formed in the joint part with the end plate part 74. As shown in FIG. Accordingly, even when the thickness of the beam 96 is reduced to reduce the refrigerant ventilation resistance in the anti-mainstream side space 20b, since the rigidity of the beam 96 can be ensured, the deformation of the intermediate tank 18 can be reduced.

Fig. 9 is a D-D sectional view of the intermediate container of Fig. 3 . That is, FIG. 9 shows the relationship between the height M of the contact surface 81 of the outer wall portion 78 , the height N of the parallel portion 22 a of the spacer 22 , and the height L of the beam 96 . As shown in FIG. 9 , by making the height N of the parallel portion 22 a smaller than the height M of the contact surface 81 , the cross-sectional area S of the refrigerant flow path 20 c is ensured. In addition, by making the height L of the beam 96 smaller than the height N of the parallel portion 22a, the rigidity of the intermediate tank 18 can be increased and the volume V of the reverse main flow side space 20b can be ensured.

FIG. 10 is a top view of the cover 82 of FIG. 1 or FIG. 4 . As shown in FIG. 10 , the cover 82 is a disc-shaped member punched out by press working. The cover 82 is formed with a plurality of (for example, four) holes 102 for the connecting element 15 penetrating in the plate thickness direction. The plurality of holes 102 are formed at equal intervals on the same circumference, corresponding to the positions and numbers of the holes 86 of the intermediate container 18 . In addition, the cover 82 is formed with a hole 104 penetrating in the plate thickness direction at the center of the plate surface. This hole 104 is used to pass the front end portion of the non-contact portion 94 of the sub-bearing 40 . More specifically, as shown in FIGS. 1 and 4 , the hole 104 is formed to have the same diameter as the outer diameter of the non-contact portion 94 of the sub-bearing 40 . That is, when the front end portion of the non-contact portion 94 is fitted into the hole 104 , the cover 82 comes into contact with the non-contact portion 94 . Furthermore, the sealing surface is formed by sandwiching the elastic body 90 in the gap between the cover 82 and the flat surface 88 .

FIG. 11 is a cross-sectional view of the elastic body 90 in FIG. 1 or FIG. 4 . As shown in FIG. 11 , the elastic body 90 is a substantially annular truncated conical disk spring formed by pressing a copper member. The elastic body 90 is arranged on the flat surface 88 along the front end outer periphery of the sub-bearing 40 as shown in FIG. 4 . That is, the elastic body 90 is sandwiched between the flat surface 88 and the cover 82 . When the elastic body 90 is arranged, the bottom surface of the elastic body 90 is in contact with the flat surface of the cover 82 . As the elastic body 90 here, a disk-shaped gasket, an O-ring, or the like can be applied. However, when using gaskets, it is better to use rubber or resin materials that are more easily deformed.

FIG. 12 is a graph showing the measurement results of the rate of change in the coefficient of performance (COP) of the refrigeration cycle when the channel cross-sectional area S of the refrigerant channel 20 c is controlled. The horizontal axis of FIG. 12 represents the ratio (S/V) of the volume V (mm ³ ) of the anti-mainstream side space 20 b to the flow channel cross-sectional area S (mm ² ) of the refrigerant flow channel 20 c. The vertical axis represents the change rate (%) of the COP of the air conditioner with respect to the ratio (S/V). In addition, the COP here refers to dividing the adjustment capability of the air conditioner by the input. In addition, relative evaluation was performed with reference to the COP when the ratio (S/V) was zero.

As shown in FIG. 12 , the rate of change of the COP of the air conditioner increases sharply as the ratio (S/V) increases from zero, and gradually decreases with a certain ratio (S/V) as a boundary. That is, at the beginning of increasing the ratio (S/V) from zero, since the amount of refrigerant passing through the flow path cross-sectional area S (mm ² ) increases as the ratio (S/V) increases, the anti-main flow side space 20b is exerted. The resonance function of the air conditioner improves the COP of the air conditioner as a result of suppressing pressure fluctuations in the discharge space 20 . However, when the ratio (S/V) is excessively increased beyond a certain value, since the division of the anti-mainstream side space 20b and the mainstream side space 20a becomes blurred, the ejection space 20 becomes enlarged as in the conventional space Since they are substantially the same, the pressure fluctuation of the discharge space 20 cannot be suppressed sufficiently, and the COP of an air conditioner falls. Also, as the ratio (S/V) increases, the effect of improving rigidity by the end plate portion 74 of the spacer member 22 decreases, and thus mechanical loss due to deformation of the end plate portion 74 increases. In view of such circumstances, it is desirable that the ratio (S/V) of the present embodiment is, for example, 0.1×10 ^-2 (mm ^-1 ) as the lower limit, for example, 2.0×10 ^-2 (mm ^-1 ) as the upper limit. within the limits. Within this range, a COP improvement effect within, for example, 1% or more of the measurement error range of a general air conditioner performance measuring device can be obtained.

As mentioned above, although one embodiment of the rotary compressor 1 to which this invention is applied was demonstrated, it is not limited to this.

FIG. 13 is a cross-sectional view showing another first example of the intermediate container 18 according to the present embodiment. As shown in FIG. 13 , in the intermediate container 18 of this example, a step having a flat surface 88 is formed on the outer peripheral wall of the sub-bearing 43 at the point that the outer peripheral wall of the sub-bearing 106 is formed to have the same diameter in the axial direction. Part of Figure 4 works differently. That is, the intermediate container 18 of this example is a container in which the height of the flat surface 88 in FIG. 4 is aligned with the connecting surface 81 . Therefore, the outer peripheral portion of the lower end surface 108 of the sub bearing 106 is in contact with the flat surface of the cover 82 . The spacer 22 here is formed to have: a parallel portion 22a whose height is smaller than the lower end surface 108 of the sub-bearing 106; an inner peripheral tapered portion 22g connecting the inner peripheral edge of the parallel portion 22a to the outer peripheral edge of the lower end surface 108; and The outer peripheral edge of the parallel portion 22 a is connected to the outer peripheral tapered portion 22 c of the inner peripheral edge of the outer wall portion 78 . Thereby, the flow path cross-sectional area S of the refrigerant flow path 20c formed between the spacer member 22 and the flat surface of the cover 82 can be ensured. In addition, although the inclination angle of the inner peripheral side taper part 22g is larger than the outer peripheral side taper part 22c, it is not limited to this, What is necessary is just to adjust as needed.

Fig. 14 is a cross-sectional view showing another second example of the intermediate container of the present embodiment. As shown in FIG. 14 , the intermediate container 18 of this example is different from that of FIG. 13 in which the refrigerant flow path 20c is formed in the entire area of the separation member 22 in that the refrigerant flow path 20c is formed in a part of the separation member 22. different. That is, the intermediate tank 18 of this example differs from the aspect of FIG. 12 in which the refrigerant flow path 20c has the same width as the spacer 22 in that the width of the refrigerant flow path 20c is smaller than that of the spacer 22 . In other words, the outer peripheral portion of the front end surface of the spacer member 22 is in contact with the flat surface of the cover 82 . The spacer 22 here is formed to have: a parallel portion 22a whose height is smaller than the lower end surface 108 of the sub-bearing 106; an inner peripheral tapered portion 22g connecting the inner peripheral edge of the parallel portion 22a to the outer peripheral edge of the lower end surface 108; The outer peripheral edge of the parallel portion 22a is inclined toward the outer peripheral tapered portion 22h of the cover 82 . Thereby, since the rigidity of the spacer member 22 increases, the rigidity of the intermediate container 18 increases as a result.

As described above, according to the present embodiment, since the intermediate container 18 has a hollow resonance function, the pressure pulsation of the intermediate pressure Pm in the intermediate container 18 is suppressed, so that the coefficient of performance (COP) of the refrigeration cycle can be improved, and it is possible to suppress the pulsation in the rotary compressor 1. Noise and vibration generated in the

Claims (4)

1. A rotary compressor, characterized in that, include: Rotary low-pressure side compression part, which compresses the refrigerant; a rotary high-pressure side compression section that compresses the refrigerant in anti-phase with respect to the compression process of the low-pressure side compression section; and an intermediate container communicating with the refrigerant discharge port of the low-pressure side compression unit and the refrigerant suction port of the high-pressure side compression unit, The inner space of the intermediate container is divided into at least two spaces by a partition member, and the refrigerant discharge port of the low-pressure side compression part and the refrigerant suction port of the high-pressure side compression part are connected in one space, and the partition The component forms a refrigerant flow path connecting the two spaces, The intermediate container has: a disc-shaped end plate; an outer wall portion standing up from the peripheral portion of the end plate portion in the axial direction to define the circumferential direction of the ejection space; a cylindrical sub-bearing standing upright in the axial direction at the center of the end plate portion; and a blocking plate that faces the end plate portion and blocks the opening on the front end side of the outer wall portion, The spacer member is a beam erected on the plate surface of the end plate part from the sub bearing on the outer peripheral wall, The beam is formed such that an axial dimension from the end plate portion is smaller than that of the outer wall portion, and forms the refrigerant flow path with the closing plate. 2. The rotary compressor of claim 1, wherein: The sub-bearing is formed by an enlarged diameter portion whose outer diameter on the side of the end plate portion is larger than that on the front end side, and an axial dimension of the spacer from the end plate portion is smaller than the enlarged diameter portion. 3. The rotary compressor according to claim 1 or 2, characterized in that, The spacer is formed on the front end side with: a parallel portion parallel to the plate surface of the end plate portion; an inner peripheral tapered portion inclined toward the sub-bearing side from the inner peripheral edge of the parallel portion toward the axial direction; and The outer peripheral side tapered portion inclined toward the outer wall portion side from the inner peripheral edge of the parallel portion toward the axial direction, The refrigerant flow path is an opening having a trapezoidal cross section defined by the parallel portion, the inner tapered portion, the outer tapered portion, and the closing plate. 4. The rotary compressor according to claim 1 or 2, characterized in that, The intermediate container is provided in the other space partitioned by the partition member: a reinforcing beam erected on the plate surface of the end plate part from the sub-bearing on the outer peripheral wall, A dimension of the reinforcement beam in the axial direction from the end plate portion is smaller than that of the spacer member.

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