EP3557066B1

EP3557066B1 - Rotary compressor and refrigeration cycle device

Info

Publication number: EP3557066B1
Application number: EP17884506.1A
Authority: EP
Inventors: FERDHY Monasry JAFET; Takuya Hirayama; Yasumitsu Nojima
Original assignee: Toshiba Carrier Corp
Current assignee: Toshiba Carrier Corp
Priority date: 2016-12-19
Filing date: 2017-12-12
Publication date: 2021-06-30
Anticipated expiration: 2037-12-12
Also published as: EP3557066A4; EP3557066A1; JP6758412B2; WO2018116912A1; CN109952439B; CN109952439A; JPWO2018116912A1

Description

[Technical Field]

Embodiments of the present invention relate to a rotary compressor and a refrigeration cycle device.

[Background Art]

In a proposed rotary compressor having two cylinders arranged in an axial direction of a rotating shaft, a first suction passage to which a working fluid is supplied from a suction pipe is provided in one of the two cylinders, and a second suction passage that branches off from the first suction passage and guides some of the working fluid to the other of the two cylinders is also provided.
Meanwhile, in the rotary compressor as described above, for example, to reduce a flow loss of the working fluid, the second suction passage is defined by an inclined hole that is inclined with respect to the axial direction of the rotating shaft. In this case, manufacturability of the rotary compressor is sometimes reduced.

[Citation List]

[Patent Literature]

[Patent Literature 1] Japanese Unexamined Utility Model Application, First Publication No. S61-33993
[Patent Literature 2] Japanese Unexamined Patent Application, First Publication No. 2005-207306
[Patent Literature 3] WO 2009/062365 A1 discloses a suction device for capacity-controlled rotary compressor, which includes a motor, an upper cylinder and a lower cylinder which are placed in a shell body of the compressor, a clapboard fixed between the cylinders, a piston provided in the responding cylinder, a gliding slab fixed in a gliding slab slot of the cylinder, an eccentric-cranksaft for driving the piston operation, bearings for supporting the eccentric-crankshaft, and a capacity valve for implementing a capacity control.
[Patent Literature 4] JP S6 224084 U discloses a main intake valve and an auxiliary intake valve in a gasoline engine.
[Patent Literature 5] US 4,826,408 A relates to a two-cylinder rotary compressor with a closed casing, a compression section, and an electric motor section, both arranged in the casing, for driving the compression section.
[Patent Literature 6] JP H08 270580 A relates to a hermetically sealed rotary compressor with an electric element in a closed container and a rotary compression element driven by a crankshaft of the electric element, and the rotary compression element is constituted of a cylinder divided into a plurality of stages via a partition plate and a piston roller provided alternately in the cylinder so as to be freely eccentrically rotated in the crank shaft.

[Summary of Invention]

[Technical Problem]

A problem to be solved by the present invention is to provide a rotary compressor and a refrigeration cycle device capable of improving manufacturability, and to increase in efficiency by reducing suction losses.

[Solution to Problem]

A rotary compressor of an embodiment includes a rotating shaft, a first cylinder, a second cylinder, and a partition plate. The rotating shaft includes a first eccentric part and a second eccentric part which are arranged in an axial direction. The first cylinder forms a first cylinder chamber in which the first eccentric part is disposed. The second cylinder formes a second cylinder chamber in which the second eccentric part is disposed. The partition plate is disposed between the first cylinder and the second cylinder. The first cylinder includes a first suction passage provided in a radial direction of the rotating shaft, the first suction passage making a suction pipe in which a working fluid flows and the first cylinder chamber communicate with each other. At least the first cylinder and the partition plate includes a second suction passage branching off from the first suction passage, the second suction passage making the first suction passage and the second cylinder chamber communicate with each other. The first cylinder includes a first suction hole provided in the axial direction, the first suction hole forming a part of the second suction passage. The partition plate includes a second suction hole provided in the axial direction, the second suction hole forming another part of the second suction passage. A center of the first suction hole is located outside in the radial direction with respect to a center of the second suction hole. At least one of an opening edge of the first suction hole which is adjacent to the partition plate and an opening edge of the second suction hole which is adjacent to the first cylinder is provided with a chamfer.

[Brief Description of Drawings]

Fig. 1 is a schematic constitution diagram of a refrigeration cycle device including a cross section of a rotary compressor of an embodiment.
Fig. 2 is a sectional view taken along F2-F2 of a compression mechanism illustrated in Fig. 1.
Fig. 3 is an enlarged sectional view illustrating a part of the compression mechanism of the embodiment.
Fig. 4 is an enlarged sectional view illustrating a part of a compression mechanism of a modification of the embodiment.

[Description of Embodiments]

Hereinafter, a rotary compressor and a refrigeration cycle device of an embodiment will be described with reference to the drawings.
First, the refrigeration cycle device will be briefly described.
Fig. 1 is a schematic constitution diagram illustrating a refrigeration cycle device 1 of the present embodiment.
As illustrated in Fig. 1, the refrigeration cycle device 1 includes a rotary compressor 2, a heat radiator 3 (e.g., a condenser) connected to the rotary compressor 2, an expansion unit 4 (e.g., an expansion valve) connected to the heat radiator 3, and a heat absorber 5 (e.g., an evaporator) connected between the expansion unit 4 and the rotary compressor 2.
The rotary compressor 2 is a so-called rotary type compressor. The rotary compressor 2 compresses, for example, a low-pressure gas refrigerant (a working fluid) introduced thereinto into a high-temperature high-pressure gas refrigerant. A specific constitution of the rotary compressor 2 will be described below.
The heat radiator 3 radiates heat from the high-temperature high-pressure gas refrigerant fed from the rotary compressor 2, and converts the high-temperature high-pressure gas refrigerant into a high-pressure liquid refrigerant.
The expansion unit 4 lowers a pressure of the high-pressure liquid refrigerant fed from the heat radiator 3, and converts the high-pressure liquid refrigerant into a low-temperature low-pressure liquid refrigerant.
The heat absorber 5 vaporizes the low-temperature low-pressure liquid refrigerant fed from the expansion unit 4, and converts the low-temperature low-pressure liquid refrigerant into a low-pressure gas refrigerant. The surroundings of the heat absorber 5 are cooled by absorbing vaporization heat from the surroundings when the low-pressure liquid refrigerant is vaporized. The low-pressure gas refrigerant passing through the heat absorber 5 is introduced into the aforementioned rotary compressor 2.
In this way, in the refrigeration cycle device 1 of the present embodiment, the refrigerant that is the working fluid circulates while undergoing a change in phase between the gas refrigerant and the liquid refrigerant, radiates heat in the process of changing its phase from the gas refrigerant to the liquid refrigerant, and absorbs heat in the process of changing its phase from the liquid refrigerant to the gas refrigerant. Heating or cooling is performed using the heat radiation or the heat absorption.
Next, a specific constitution of the aforementioned rotary compressor 2 will be described.
The rotary compressor 2 of the present embodiment includes a compressor main body 11 and an accumulator 12.
The accumulator 12 is a so-called gas-liquid separator. The accumulator 12 is provided between the heat absorber 5 and the compressor main body 11 that have been described above. The accumulator 12 is connected to the compressor main body 11 through the suction pipe 21. The accumulator 12 supplies the gas refrigerant vaporized by the heat absorber 5 to the compressor main body 11 through the suction pipe 21.
The compressor main body 11 includes a rotating shaft 31, an electromotor 32 that rotates the rotating shaft 31, a compression mechanism 33 that compresses a gas refrigerant by means of the rotation of the rotating shaft 31, and a cylindrical airtight vessel 34 in which the rotating shaft 31, electromotor 32, and compression mechanism 33 are housed.
The rotating shaft 31 and the airtight vessel 34 are disposed coaxially with the axial center (the axis) O of the rotating shaft 31. The axial center O of the rotating shaft 31 is the center (the rotational center) of the rotating shaft 31. The electromotor 32 is disposed on one end side (an upper side in Fig. 1) of the airtight vessel 34 in a direction along the axial center O. The compression mechanism 33 is disposed on the other end side (a lower side in Fig. 1) of the airtight vessel 34 in the direction along the axial center O. In the following description, the direction along the axial center O is referred to as an axial direction Z of the rotating shaft 31, a direction that is perpendicular to the axial center O and is radially away from the axial center O is referred to as a radial direction R of the rotating shaft 31, and a direction around the axial center O at a fixed distance from the axial center O is referred to as a circumferential direction θ of the rotating shaft 31 (see Fig. 2).
The rotating shaft 31 passes through the electromotor 32 and extends into the compression mechanism 33 in the axial direction Z. The rotating shaft 31 includes a first eccentric part 41 and a second eccentric part 42 which are arranged in the axial direction Z. The first eccentric part 41 is provided at a position of the rotating shaft 31 which corresponds to a first cylinder 51 (to be described below) of the compression mechanism 33. Similarly, the second eccentric part 42 is provided at a position of the rotating shaft 31 which corresponds to a second cylinder 52 (to be described below) of the compression mechanism 33. Each of the first eccentric part 41 and the second eccentric part 42 has, for example, a columnar shape in the axial direction Z. The first eccentric part 41 and the second eccentric part 42 are eccentric to the axial center O in the radial direction R by the same amount. The first eccentric part 41 and the second eccentric part 42 are formed, for example, in the same form and size in a top view in the axial direction Z, and are disposed, for example, with a phase difference of 180° in the circumferential direction θ.
The electromotor 32 is, for example, a so-called inner rotor DC brushless motor. To be specific, the electromotor 32 includes a stator 36 and a rotor 37. The stator 36 is formed in a tubular shape, and is fixed to an inner wall surface of the airtight vessel 34 by shrink fitting or the like. The rotor 37 is disposed inside the stator 36. An upper portion of the rotating shaft 31 is coupled to the rotor 37. A current is supplied to coils provided in the stator 36, and thereby the rotor 37 rotatably drives the rotating shaft 31.
Next, the compression mechanism 33 will be described.
The compression mechanism 33 includes a plurality of cylinders (the first cylinder 51 and the second cylinder 52), a partition plate 53, a main bearing 54, an auxiliary bearing 55, and a plurality of rollers (a first roller 56 and a second roller 57).
The first cylinder 51 and the second cylinder 52 are arranged in the axial direction Z at a distance from each other. Each of the first cylinder 51 and the second cylinder 52 is formed in a tubular shape that opens in the axial direction Z. Thus, an internal space serving as a first cylinder chamber 51a is formed in the first cylinder 51. The first eccentric part 41 of the rotating shaft 31 is disposed in the first cylinder chamber 51a. Similarly, an internal space serving as a second cylinder chamber 52a is formed in the second cylinder 52. The second eccentric part 42 of the rotating shaft 31 is disposed in the second cylinder chamber 52a. A supply structure in which a gas refrigerant is supplied to the first cylinder chamber 51a and the second cylinder chamber 52a will be described below.
The partition plate 53 is disposed between the first cylinder 51 and the second cylinder 52 in the axial direction Z, and is sandwiched between the first cylinder 51 and the second cylinder 52. The partition plate 53 faces the first cylinder chamber 51a in the axial direction Z, and defines one surface of the first cylinder chamber 51a. Similarly, the partition plate 53 faces the second cylinder chamber 52a in the axial direction Z, and defines one surface of the second cylinder chamber 52a. Further, an opening through which the rotating shaft 31 passes in the axial direction Z is provided in the partition plate 53.
The main bearing 54 is located on a side opposite to the partition plate 53 with respect to the first cylinder 51. The main bearing 54 faces the first cylinder chamber 51a from one side opposite to the partition plate 53, and defines the other surface of the first cylinder chamber 51a. On the other hand, the auxiliary bearing 55 is located on a side opposite to the partition plate 53 with respect to the second cylinder 52. The auxiliary bearing 55 faces the second cylinder chamber 52a from the other side opposite to the partition plate 53, defines the other surface of the second cylinder chamber 52a. The aforementioned rotating shaft 31 passes through the first cylinder 51, the second cylinder 52, and the partition plate 53, and is rotatably supported by the main bearing 54 and the auxiliary bearing 55.
Each of the first roller 56 and the second roller 57 is formed in a tubular shape in the axial direction Z. The first roller 56 is fitted into the first eccentric part 41, and is disposed in the first cylinder chamber 51a. Similarly, the second roller 57 is fitted into the second eccentric part 42, and is disposed in the second cylinder chamber 52a. Gaps, by which relative rotation of the rollers 56 and 57 relative to the eccentric parts 41 and 42 is allowed, are provided between inner circumferential surfaces of the rollers 56 and 57 and outer circumferential surfaces of the eccentric parts 41 and 42. That is, the term "fitted" used herein also includes a case where there is a gap by which mutual rotation is allowed between two members. The first roller 56 and the second roller 57 are eccentrically rotated in the cylinder chambers 51a and 52a while bringing outer circumferential surfaces of the rollers 56 and 57 into slide contact with inner circumferential surfaces of the cylinders 51 and 52 in association with the rotation of the rotating shaft 31 (see Fig. 2).
Next, internal constitutions of the cylinders 51 and 52 will be described.
Here, the internal constitution of the first cylinder 51 and the internal constitution of the second cylinder 52 are substantially identical to each other excluding portions that differ depending on a phase difference between the eccentric parts 41 and 42 and a phase difference between the rollers 56 and 57 and portions related to suction passages 71 and 72 to be described below. For this reason, here, the internal constitution of the first cylinder 51 will be described as a representative.
Fig. 2 is a sectional view taken along line F2-F2 of the compression mechanism 33 illustrated in Fig. 1.
As illustrated in Fig. 2, a vane groove 58, which extends outward in the radial direction R, is provided in the first cylinder 51. A vane 59, which can slide in the radial direction R, is inserted into the vane groove 58. The vane 59 is biased inward in the radial direction R by a biasing means (not shown), and a tip thereof is in contact with the outer circumferential surface of the first roller 56 in the first cylinder chamber 51a. Thus, the vane 59 partitions an interior of the first cylinder chamber 51a into a suction chamber 61 and a compression chamber 62 in the circumferential direction θ. The vane 59 moves forward/backward in the first cylinder chamber 51a in association with eccentric rotation of the first roller 56. For this reason, when the first roller 56 is eccentrically rotated in the first cylinder chamber 51a, a compressing action of compressing a gas refrigerant in the first cylinder chamber 51a is performed by the eccentric rotation of the first roller 56 and the forward/backward movement of the vane 59 associated therewith. The gas refrigerant compressed in the first cylinder chamber 51a is discharged into the airtight vessel 34 through a discharge groove (not shown) or the like of the first cylinder 51.
Next, the supply structure in which the gas refrigerant (the working fluid) is supplied to the first cylinder 51 and the second cylinder 52 will be described. As illustrated in Fig. 1, in the rotary compressor 2 of the present embodiment, the suction pipe 21 is connected only to one cylinder 51 of the two cylinders 51 and 52 arragnged in the axial direction Z, and a branch channel for guiding some of the gas refrigerant supplied from the suction pipe 21 to the cylinder 51 into the other cylinder 52 is provided in the compression mechanism 33. This will be described below in detail.
In the present embodiment, the suction pipe 21 in which the gas refrigerant flows from the accumulator 12 is connected to the first cylinder 51. A first suction passage 71, which makes the suction pipe 21 and the first cylinder chamber 51a communicate with each other, is provided in the first cylinder 51 in the radial direction R. The term "provided in the radial direction" used herein means, for example, that a hole opens in the radial direction R. For this reason, "provided in the radial direction" may be rephrased as "provided parallel to the radial direction" or "open in the radial direction."
The first suction passage 71 is, for example, a hole that is provided in the first cylinder 51 in the radial direction R. The first suction passage 71 passes, for example, from an outer circumferential surface of the first cylinder 51 to the inner circumferential surface of the first cylinder 51 by which the first cylinder chamber 51a is defined. A gas refrigerant is directly supplied from the suction pipe 21 to the first suction passage 71. The first suction passage 71 guides some of the gas refrigerant supplied from the suction pipe 21 into the suction chamber 61 of the first cylinder chamber 51a.
Further, a second suction passage 72 branching off from the first suction passage 71 is provided in the compression mechanism 33. The second suction passage 72 is provided over the first cylinder 51, the partition plate 53, and the second cylinder 52, and makes the first suction passage 71 and the second cylinder chamber 52a communicate with each other. The second suction passage 72 guides some of the gas refrigerant flowing in the first suction passage 71 into the second cylinder chamber 52a.
Next, the second suction passage 72 will be described in detail.
Fig. 3 is an enlarged sectional view illustrating a part of the compression mechanism 33 of the present embodiment.
As illustrated in Fig. 3, the second suction passage 72 is made up of, for example, a first suction hole 81 provided in the first cylinder 51, a second suction hole 82 provided in the partition plate 53, and a refrigerant channel 83 provided in the second cylinder 52.
The first suction hole 81 is provided in the first cylinder 51 in the axial direction Z. The term "provided in the axial direction" used herein means, for example, that a hole opens in the axial direction Z. For this reason, "provided in the axial direction" may be rephrased as "provided parallel to the axial direction" or "open in the axial direction." The first suction hole 81 is, for example, a round hole in which a cross-sectional shape that opens in the axial direction Z is a circular shape. The first suction hole 81 passes from the first suction passage 71 to a surface (e.g., a lower surface) of the first cylinder 51 which faces the partition plate 53 in the axial direction Z. The first suction hole 81 makes the first suction passage 71 communicate with the second suction hole 82 provided in the partition plate 53.
A first chamfer 91 is provided on an opening edge 81a of the first suction hole 81 which is adjacent to the partition plate 53. The first chamfer 91 is, for example, provided throughout the circumference of the opening edge 81a. Thus, the opening edge 81a has an inclined portion (a diameter enlarged portion) that is inclined with respect to the axial direction Z. Thus, a cross-sectional area (an opening area) of the first suction hole 81 is increased by the first chamfer 91.
The second suction hole 82 is provided in the partition plate 53 in the axial direction Z. The second suction hole 82 is, for example, a round hole which extends in the axial direction Z and in which a cross-sectional shape that opens in the axial direction Z is a circular shape. The second suction hole 82 passes from a surface of the partition plate 53 which faces the first cylinder 51 (e.g., an upper surface) to a surface of the partition plate 53 which faces the second cylinder 52 (e.g., a lower surface) in the axial direction Z. The second suction hole 82 makes the first suction hole 81 of the first cylinder 51 to communicate with the refrigerant channel 83 of the second cylinder 52. An inner diameter of the second suction hole 82 is substantially the same as, for example, an inner diameter of the first suction hole 81. However, the inner diameter of the second suction hole 82 may be larger or smaller than that of the first suction hole 81.
A second chamfer 92 is provided on an opening edge 82a of the second suction hole 82 which is adjacent to the first cylinder 51. The second chamfer 92 is, for example, provided throughout the circumference of the opening edge 82a. Further, a third chamfer 93 is provided on an opening edge 82b of the second suction hole 82 which faces the second cylinder 52. The third chamfer 93 is, for example, provided throughout the circumference of the opening edge 82b. Thus, each of the opening edges 82a and 82b has an inclined portion (a diameter enlarged portion) that is inclined with respect to the axial direction Z. Thus, a cross-sectional area (an opening area) of the second suction hole 82 is increased by each of the second chamfer 92 and the third chamfer 93.
The refrigerant channel 83 is, for example, a groove provided in the second cylinder 52. For example, the refrigerant channel 83 passes from a surface of the second cylinder 52 which faces the partition plate 53 (e.g., an upper surface) to the inner circumferential surface of the second cylinder 52 by which the second cylinder chamber 52a is defined. The refrigerant channel 83 makes the second suction hole 82 of the partition plate 53 communicate with the second cylinder chamber 52a. The refrigerant channel 83 is, for example, provided in an inclined direction with respect to the axial direction Z. The refrigerant channel 83 has an inclined surface 83a that is inclined with respect to the axial direction Z.
With the constitution as described above, some of the gas refrigerant flowing in the first suction passage 71 is guided to a suction chamber 61 of the second cylinder chamber 52a through the first suction hole 81 provided in the first cylinder 51, the second suction hole 82 provided in the partition plate 53, and the refrigerant channel 83 provided in the second cylinder 52.
Next, a position at which the second suction hole 82 is disposed will be described.
As illustrated in Fig. 3, in the present embodiment, the first suction hole 81 and the second suction hole 82 are disposed at mutually shifted positions in the radial direction R of the rotating shaft 31. In the present embodiment, the center 81c of the first suction hole 81 is located outside in the radial direction R with respect to the center 82c of the second suction hole 82. The center 81c of the first suction hole 81 is, for example, the center of the first suction hole 81 in the radial direction R of the rotating shaft 31. The center 82c of the second suction hole 82 is, for example, the center of the second suction hole 82 in the radial direction R of the rotating shaft 31.
Further, from another point of view, the first suction hole 81 has a first end 81e1 that is located furthest outward in the first suction hole 81 in the radial direction R except for the chamfer 91, and a first end 81e2 that is located furthest inward in the first suction hole 81 in the radial direction R except for the chamfer 91. Similarly, the second suction hole 82 has a first end 82e1 that is located furthest outward in the second suction hole 82 in the radial direction R except for the chamfers 92 and 93, and a second end 82e2 that is located furthest inward in the second suction hole 82 in the radial direction R except for the chamfers 92 and 93. The first end 81e1 of the first suction hole 81 is located outside in the radial direction R with respect to the first end 82e1 of the second suction hole 82. Further, the second end 81e2 of the first suction hole 81 is located outside in the radial direction R with respect to the second end 82e2 of the second suction hole 82.
Next, several dimensional relationships related to the first suction hole 81 and the second suction hole 82 are shown. First, L1, L2, L3, L4, L5, Rc, R1, R2, and R3 are defined as a premise. As illustrated in Fig. 3, L1 is a distance in the radial direction R between the axial center O of the rotating shaft 31 and the center 81c of the first suction hole 81 in the radial direction R. L2 is a distance in the radial direction R between the axial center O of the rotating shaft 31 and the center 82c of the second suction hole 82 in the radial direction R. L3 is a distance in the axial direction Z between an interface (a junction plane) B between the first cylinder 51 and the partition plate 53 and the center 71c of the first suction passage 71 in the axial direction Z. L4 is a thickness of the partition plate 53 in the axial direction Z. L5 is a distance in the radial direction R between the axial center O of the rotating shaft 31 and the center 83c (to be described below) of the refrigerant channel 83 in the radial direction R. Rc is a radius of the first cylinder chamber 51a. R1 is a radius of the first suction passage 71 in the axial direction Z. R2 is a radius of the first suction hole 81 in the radial direction R. R3 is a radius of the second suction hole 82 in the radial direction R.
The axial center O of the rotating shaft 31 is substantially coincident with the center of the first cylinder chamber 51a in the radial direction R and the center of the second cylinder chamber 52a in the radial direction R. For this reason, "the axial center O of the rotating shaft 31" may be rephrased as "the center (the inner diameter center) of the first cylinder chamber 51a in the radial direction R" or "the center (the inner diameter center) of the second cylinder chamber 52a in the radial direction R." Further, the refrigerant channel 83 has a first end 83e1 located on an outermost side of the refrigerant channel 83 in the radial direction R, and a second end 83e2 located on an innermost side of the refrigerant channel 83 in the radial direction R. "The center 83c of the refrigerant channel 83 in the radial direction R" is a point located at an equal distance from the first end 83el and the second end 83e2 in the radial direction R.
In a case where the various dimensions are defined as described above,
when C1=L1-R2-Rc, C2=L3-R1, and C3=L1-L2, each of C1 and C2 is greater than or equal to C3. Here, as illustrated in Fig. 3, C1 is equivalent to a minimum wall thickness in the radial direction R between an inner surface of the first suction hole 81 and the inner circumferential surface of the first cylinder 51 by which the first cylinder chamber 51a is defined. C2 is equivalent to a minimum wall thickness in the axial direction Z between the first suction passage 71 and the partition plate 53. C3 is equivalent to a shift amount in the radial direction R between the center 81c of the first suction hole 81 and the center 82c of the second suction hole 82.
Further, in the case where the various dimensions are defined as described above,
when $C 2 = L 3 - R 1$
and $C 3 = L 1 - L 2,$
$C 2 / C 3 < L 4 / R 3 .$
Further, in the case where the various dimensions are defined as described above,
L1>L2≥L5. That is, in the present embodiment, the center 82c of the second suction hole 82 and the center 83c of the refrigerant channel 83 are located at substantially the same position in the radial direction R. Alternatively, the center 82c of the second suction hole 82 may be located outside in the radial direction R with respect to the center 83c of the refrigerant channel 83.
In the present embodiment, a cross section of the second suction passage 72 on the interface B between the first cylinder 51 and the partition plate 53 has a spindle shape that is defined by a portion where the first suction hole 81 and the second suction hole 82 overlap each other in the axial direction Z. A cross-sectional area (an opening area) of the cross section (the spindle-shaped cross section) of the second suction passage 72 on the interface B is, for example, larger than a cross-sectional area (an opening area) of the first suction passage 71 on a cross section parallel to the axial direction Z.
Further, from another point of view, a cross-sectional area (an opening area) of the first suction hole 81 on a cross section parallel to the radial direction R is larger than the cross-sectional area (the opening area) of the first suction passage 71 on the cross section parallel to the axial direction Z. In other words, as illustrated in Fig. 2, R2>R1. Further, a cross-sectional area (an opening area) of the second suction hole 82 on a cross section parallel to the radial direction R is larger than the cross-sectional area (the opening area) of the first suction passage 71 on the cross section parallel to the axial direction Z. In other words, R3>R1.
Next, an action of the rotary compressor 2 of the present embodiment will be described.
When the rotary compressor 2 is driven and the rotating shaft 31 is rotated, the first roller 56 and the second roller 57 are eccentrically rotated in the first cylinder chamber 51a and the second cylinder chamber 52a. Thus, gas refrigerants in the first and second cylinder chambers 51a and 52a are compressed and discharged into the airtight vessel 34 through the discharge grooves of the first and second cylinders 51 and 52.
Further, when pressures of the suction chambers 61 of the first and second cylinder chambers 51a and 52a are reduced by eccentric rotations of the first and second rollers 56 and 57, a gas refrigerant is supplied from the accumulator 12 through the suction pipe 21. Some of the gas refrigerant supplied from the suction pipe 21 is supplied to the first cylinder chamber 51a through the first suction passage 71 provided in the first cylinder 51. Further, yet some of the gas refrigerant flowing in the suction pipe 21 enters the first suction passage 71, and then flows into the second suction passage 72, thereby being supplied to the second cylinder chamber 52a. Here, in the present embodiment, the center 81c of the first suction hole 81 serving as an inlet of the second suction passage 72 is located outside in the radial direction R with respect to the center 82c of the second suction hole 82. For this reason, in a case where a combination of the first suction hole 81 and the second suction hole 82 is viewed, the second suction passage 72 has a constitution in which it is similar to an inclined hole inclined with respect to the axial direction Z to turn to the second cylinder chamber 52a. For this reason, a gas refrigerant can flow from the first suction passage 71 toward the second cylinder chamber 52a while being inclined with respect to the axial direction Z. Thus, the gas refrigerant inside the first suction passage 71 can relatively smoothly flow into the second cylinder chamber 52a.
According to this constitution, manufacturability can be improved while making performance of the rotary compressor 2 high. That is, a rotary compressor using, for example, carbon dioxide or the like as a working fluid may have a constitution in which, since the working fluid has a relatively high pressure, a suction pipe is connected to one of two cylinders, and a branch channel for guiding a gas refrigerant to the other cylinder is provided. In this case, when the branch channel is defined by a suction hole parallel to the axial direction of the rotating shaft, a suction channel loss of the working fluid may be large, and a reduction in performance of the rotary compressor may be incurred. Therefore, it is conceivable that the branch channel is defined by the inclined hole inclined with respect to the axial direction, thereby reducing the suction channel loss. However, the rotary compressor in which the inclined hole is provided may have low manufacturability and incur a reduction in quality due to an increase in manufacturing costs, generation of burr, or the like.
Thereofore, in the present embodiment, the center 81c of the first suction hole 81 is located outside in the radial direction R with respect to the center 82c of the second suction hole 82. According to this constitution, even if the first and second suction holes 81 and 82 are suction holes provided in the axial direction Z, a branch angle of the second suction passage 72 with respect to the first suction passage 71 can be inclined with respect to the axial direction Z. Thus, a structure similar to the case where the inclined hole is provided can be realized, and the suction channel loss can be reduced. First, since the first and second suction holes 81 and 82 are the suction holes provided in the axial direction Z, when compared to the inclined hole, manufacturability is good, and a reduction in quality due to generation of burr or the like can also be prevented. For this reason, the rotary compressor 2 having high performance, high quality, and a low cost can be provided.
In the present embodiment, the chamfers 91 and 92 are provided on the opening edge 81a of the first suction hole 81 which is adjacent to the partition plate 53 and the opening edge 82a of the second suction hole 82 which is adjacent to the first cylinder 51. Thus, even in the case where the first suction hole 81 and the second suction hole 82 are shifted, a channel cross-sectional area at a connection portion between the first suction hole 81 and the second suction hole 82 can be greatly secured. Thus, it is possible to reduce a suction channel loss that can occur in the case where the first suction hole 81 and the second suction hole 82 are shifted, and further provide a high-performance compressor. Even in a case where only any one of the opening edge 81a of the first suction hole 81 and the opening edge 82a of the second suction hole 82 is provided with a chamfer, a reduction in suction channel loss can be expected.
In the present embodiment, a cross-sectional area of the second suction passage 72 (an cross-sectional area when viewed in the axial direction Z) on the interface B between the first cylinder 51 and the partition plate 53 is larger than that of the first suction passage 71 on the cross section in the axial direction Z. According to this constitution, even in the case where the first suction hole 81 and the second suction hole 82 are shifted, a minimum cross-sectional area of the second suction passage 72 can be made larger than or equal to a cross-sectional area of the first suction passage 71. Thus, the suction channel loss can be further reduced.
In the present embodiment, in the case where various dimensions are defined as described above, when C1=L1-R2-Rc, C2=L3-R1, and C3=L1-L2, each of C1 and C2 greater than or equal to C3. According to this constitution, each of C1 and C2 greater than or equal to C3, it is easy to secure necessary rigidity at a suction passage portion of the first cylinder 51 where rigidity is readily reduced. Thus, it is possible to curb deformation of the first cylinder 51 and provide the rotary compressor 2 having higher reliability and quality.
In the present embodiment, in the case where various dimensions are defined as described above, when C2=L3-R1 and C3=L1-L2, C2/C3<L4/R3. According to this constitution, in a case where a virtual line Q, which connects a branch starting point center P of the second suction passage 72 and the center 82c of the second suction hole 82 on the interface B, is drawn, an inclination of the virtual line Q with respect to a central line of the first suction passage 71 in the radial direction R can be reduced. Thus, a suction channel loss can be further reduced at branch portions of the first suction passage 71 and the second suction passage 72. Further, the first and second suction holes 81 and 82 are desirably round holes in which cross-sectiona shapes thereof open in the axial direction Z are circular in view of workability, but the cross-sectional shapes thereof may be oval or the like.
In addition, in the present embodiment, the refrigeration cycle device 1 capable of improving manufacturability because it includes the aforementioned rotary compressor 2 can be provided.
Next, a modification of the above embodiment will be described. The present modification is different from the above embodiment in that a refrigerant channel 83 of a second cylinder 52 is a groove parallel to the axial direction Z. Another constitution to be described below is substantially the same as the constitution of the above embodiment. For this reason, components having identical or similar functions are given the same reference signs, and description thereof will be omitted.
Fig. 4 is an enlarged view illustrating a part of a compression mechanism 33 of a rotary compressor 2 of a modification of the embodiment.
As illustrated in Fig. 4, in the present modification, the refrigerant channel 83 of the second cylinder 52 is, for example, a groove provided in the second cylinder 52 in the axial direction Z. The refrigerant channel 83 passes, for example, from a surface (e.g., an upper surface) of the second cylinder 52 which faces a partition plate 53 to the opposite surface (e.g., a lower surface) of the second cylinder 52 which faces an auxiliary bearing 55. A downstream end of the refrigerant channel 83 is blocked by the auxiliary bearing 55.
In the present modification, the center 82c of a second suction hole 82 is located outside in the radial direction R with respect to the center 83c of the refrigerant channel 83. In other words, in a case where various dimensions are defined as in the above embodiment, a relationship of L2>L5 is satisfied. Specifically, in the present modification, a relationship of LI>L2>L5 is satisfied.
According to this constitution, even if the first suction hole 81, the second suction hole 82, and the refrigerant channel 83 are suction holes or grooves provided in the axial direction Z, a branch angle of a second suction passage 72 with respect to a first suction passage 71 can be inclined with respect to the axial direction Z. Thus, like the above embodiment, manufacturability can be improved while making performance of the rotary compressor 2 high.
In the present modification, the refrigerant channel 83 is also a groove parallel to the axial direction Z. For this reason, all of a first cylinder 51, the partition plate 53, and the second cylinder 52 can be formed only by working in a vertical direction. For this reason, a positioning method during component working is facilitated, and an improvement in working accuracy can be expected.

(Reference example)

A reference example for the above embodiment and the above modification will be described.
In the reference example, like the above modification, the center 82c of a second suction hole 82 is located outside in the radial direction R with respect to the center 83c of a refrigerant channel 83. In other words, in a case where various dimensions are defined as in the above embodiment, a relationship of L2>L5 is satisfied. The refrigerant channel 83 may be a groove provided in the axial direction Z as in the above modification, or a groove inclined with respect to the axial direction Z as in the above embodiment.
Meanwhile, in the reference example, the center 81c of a first suction hole 81 and the center 82c of the second suction hole 82 are located at substantially the same position in the radial direction R. That is, in the reference example, a relationship of L1=L2>L5 is satisfied. Even with this constitution, in comparison with a case where the three centers that are the center 81c of the first suction hole 81, the center 82c of the second suction hole 82, and the center 83c of the refrigerant channel 83 are located at substantially the same position in the radial direction R, a suction channel loss can be reduced. Thus, manufacturability can be improved while making performance of the rotary compressor 2 high.
The rotary compressors 2 of one embodiment, one modification, and one reference example have been described above. However, the embodiment is not limited to the above examples. For example, the above embodiment has covered the example in which the first cylinder 51 in which the first suction passage 71 is provided is disposed above and the second cylinder 52 to which the gas refrigerant is supplied through the second suction passage 72 is disposed below. However, the rotary compressor 2 is not limited to the above example, and may have a constitution in which the first cylinder 51 in which the first suction passage 71 is provided is disposed below and the second cylinder 52 to which the gas refrigerant is supplied through the second suction passage 72 is disposed above. Further, a rotary compressor of a swing type in which a blade and a roller are integrated or a type in which three or more cylinders are provided can also obtain the same effect.
According to at least one embodiment described above, the first cylinder includes the first suction hole that is provided in the axial direction of the rotating shaft and forms a part of the second suction passage, the partition plate includes the second suction hole that is provided in the axial direction and forms another part of the second suction passage, and the center of the first suction hole is disposed outside in the radial direction of the rotating shaft with respect to the center of the second suction hole. According to this constitution, manufacturability can be improved.

[Reference Signs List]

1 Refrigeration cycle device
2 Rotary compressor
3 Heat radiator
4 Expansion unit
5 Heat absorber
21 Suction pipe
31 Rotary shaft
41 First eccentric part
42 Second eccentric part
51 First cylinder
51a First cylinder chamber
52 Second cylinder
52a Second cylinder chamber
53 Partition plate
71 First suction passage
72 Second suction passage
81 First suction hole
81a Opening edge
82 Second suction hole
82a Opening edge
83 Refrigerant channel
91 Chamfer
92 Chamfer
B Interface
O Axial center of rotating shaft
Z Axial direction
R Radial direction

Claims

A rotary compressor (2) comprising:
a rotating shaft (31) including a first eccentric part (41) and a second eccentric part (42), the first eccentric part (41) and the second eccentric part (42 being arranged in an axial direction (Z);

a first cylinder (51) forming a first cylinder chamber (51a) in which the first eccentric part (41) is disposed;

a second cylinder (52) forming a second cylinder chamber (52a) in which the second eccentric part (42) is disposed; and

a partition plate (53) disposed between the first cylinder (51) and the second cylinder (52),

wherein

the first cylinder (51) includes a first suction passage (71) provided in a radial direction (R) of the rotating shaft (31), the first suction passage (71) making a suction pipe (21) in which a working fluid flows and the first cylinder chamber (51a) communicate with each other,

at least the first cylinder (51) and the partition plate (53) includes a second suction passage (72) branching off from the first suction passage (71), the second suction passage (72) making the first suction passage (71) and the second cylinder chamber (52a) communicate with each other,

the first cylinder (51) includes a first suction hole (81) provided in the axial direction (Z), the first suction hole (81) forming a part of the second suction passage (72),

the partition plate (53) includes a second suction hole (82) provided in the axial direction (Z), the second suction hole (82) forming another part of the second suction passage (72), and

a center of the first suction hole (81) is located outside in the radial direction (R) with respect to a center (82c) of the second suction hole (82),

characterized in that

at least one of an opening edge (81a) of the first suction hole (81) which is adjacent to the partition plate (53) and an opening edge (82a) of the second suction hole (82) which is adjacent to the first cylinder (51) is provided with a chamfer (91, 92).
The rotary compressor (2) according to claim 1, wherein
when a distance between an axial center (O) of the rotating shaft (31) and the center (81c) of the first suction hole (81) in the radial direction (R) is defined as L1,
a distance between the axial center (O) of the rotating shaft (31) and the center (82c) of the second suction hole (82) in the radial direction (R) is defined as L2,
a distance in the axial direction (Z) between an interface between the first cylinder (51) and the partition plate (53) and the center (71c) of the first suction passage (71) in the axial direction (Z) is defined as L3,
a radius of the first cylinder chamber (51a) is defined as Rc,
a radius of the first suction passage (71) is defined as R1, and
a radius of the first suction hole (81) is defined as R2, and
when C1=L1-R2-Rc, $C 2 = L 3 - R 1,$
and $C 3 = L 1 - L 2,$
each of C1 and C2 is greater than or equal to C3.
The rotary compressor (2) according to claim 1, wherein
when a distance between an axial center (O) of the rotating shaft (31) and the center (81c) of the first suction hole (81) in the radial direction (R) is defined as L1,
a distance between the axial center (O) of the rotating shaft (31) and the center (82c) of the second suction hole (82) in the radial direction (R) is defined as L2,
a distance in the axial direction (Z) between an interface between the first cylinder (51) and the partition plate (53) and the center (71c) of the first suction passage (71) in the axial direction (Z) is defined as L3,
a thickness of the partition plate (53) in the axial direction (Z) is defined as L4, a radius of the first suction passage (71) is defined as R1, and
a radius of the second suction hole (82) is defined as R3, and
when C2=L3-R1, and $C 3 = L 1 - L 2,$
$C 2 / C 3 < L 4 / R 3 .$
The rotary compressor (2) according to any one of claims 1 to 3, wherein
the second cylinder (52) includes a refrigerant channel (83) forming still another part of the second suction passage (72), and
when the distance between an axial center (O) of the rotating shaft (31) and the center (81c) of the first suction hole (81) in the radial direction (Z) is defined as L1,
the distance between the axial center (O) of the rotating shaft (31) and the center (82c) of the second suction hole (82) in the radial direction (R) is defined as L2, and
a distance between the axial center (O) of the rotating shaft (31) and a center (83c) of the refrigerant channel (83) in the radial direction (R) is defined as L5,
L1>L2≥L5.
A refrigeration cycle device (1) comprising:
the rotary compressor (2) according to any one of claims 1 to 4;

a heat radiator (3) connected to the rotary compressor (2);

an expansion unit (4) connected to the heat radiator (3); and

a heat absorber (5) connected between the expansion unit (4) and the rotary compressor (2).