JP2009264134A - Parallel rotary compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To obtain a parallel rotary compressor that realizes reduction in axial size of a drive shaft and reduction in frictional loss by cantilevering the drive shaft. <P>SOLUTION: First and second cylinders 11, 21 are arranged side by side in the axial direction of the drive shaft 5 with a partition plate 40 interposed therebetween so as to close one of the openings of each of first and second compression chambers 14, 24. A bearing 6 is so disposed as to close the other opening of the first compression chamber 14 of the first cylinder 11. An end plate 41 is so disposed as to close the other opening of the second compression chamber 24 of the second cylinder 21. The drive shaft 5 is cantilevered by the bearing 6 so as to extend through the first and second cylinders 11, 21. First and second eccentric parts 7, 8, first and second vanes, first and second suction passages 16, 26 and first and second discharge passages 17, 27 of first and second compression mechanisms 10, 20 are formed at positions displaced at 180° from each other about the axis of the drive shaft 5, as viewed from the axial direction of the drive shaft 5. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a parallel rotary compressor in which a plurality of compression mechanisms are arranged in parallel in the axial direction of a rotating shaft.

  In the conventional rotary compressor, the rotation shaft is pivotally supported by the upper support member and the lower support member, and the first and second rotation elements are arranged in parallel in the axial direction of the rotation shaft between the upper support member and the lower support member. Then, the rotation shaft is driven to rotate by the drive element, and the refrigerant is compressed by the first and second rotation elements (see, for example, Patent Document 1).

JP 2004-156539 A

  In the conventional rotary compressor, the rotation shaft is supported by the upper support member and the lower support member arranged on both sides of the first and second rotation elements arranged in parallel in the axial direction of the rotation shaft. There is a problem that the frictional loss increases as the size in the axial direction increases.

  The present invention has been made to solve the above-described problems, and is a parallel rotary compression that realizes reduction of the axial size of the drive shaft and reduction of friction loss by supporting the rotating shaft in a cantilevered manner. The purpose is to get a chance.

  The parallel rotary compressor according to the present invention includes a hermetic shell, an electric motor housed in the hermetic shell, a drive shaft that is rotationally driven by the electric motor, and the drive shaft that is coaxial with the drive shaft in the hermetic shell. And n pairs (where n is a positive integer) of compression mechanisms arranged in parallel in the axial direction of the shaft, and compresses the low-pressure refrigerant to a high pressure by each of the n pairs of compression mechanisms. Each of the n pairs of compression mechanism portions is eccentrically disposed on the drive shaft and disposed in the cylinder, and is fitted into the eccentric portion in an externally fitted state. A rolling piston, a vane that abuts on an outer peripheral surface of the rolling piston and partitions a compression chamber defined by the cylinder and the rolling piston into a low pressure side and a high pressure side, and the compression in proximity to the vane. It opens to the low pressure side of the room Has a suction passage formed in the cylinder, a discharge passage formed in the cylinder so as to open the high pressure side of the compression chamber adjacent to the vane, to. The cylinder is arranged side by side in the axial direction of the drive shaft with the partition plate interposed therebetween so as to block one opening of the compression chamber, and a bearing is provided at one side end of the drive shaft in the axial direction. The other opening of the compression chamber of the cylinder is disposed so as to close the other opening of the compression chamber of the cylinder located, and the end plate is located at the other end in the axial direction of the drive shaft. It is arrange | positioned so that it may be closed. Further, the drive shaft is cantilevered by the bearing, the cylinder is inserted, and the eccentric portion, the vane, the suction passage, and the discharge passage in the compression mechanism portion that forms a pair of the n pairs of compression mechanism portions. Is formed at a position shifted by 180 ° around the axis of the drive shaft when viewed from the axial direction of the drive shaft.

According to this invention, since the drive shaft is cantilevered by the bearing, a bearing that supports the other end side of the drive shaft in the axial direction is not required. Therefore, the axial size of the drive shaft of the parallel rotary compressor is reduced, and the friction loss between the bearing supporting the other end side of the drive shaft in the axial direction and the drive shaft is eliminated, and the friction loss is reduced.
Further, since the eccentric portion, vane, suction passage and discharge passage in the compression mechanism portion forming a pair are formed at positions shifted by 180 ° around the axis of the drive shaft when viewed from the axial direction of the drive shaft, A series of compression processes in a pair of compression mechanisms are performed at the same timing. Therefore, the gas load acting on the drive shaft increases or decreases at the same timing, and the vectors of the gas load acting on the drive shaft are always in directions opposite to each other by 180 °. As a result, the gas loads acting on the drive shaft by the compression process of the paired compression mechanism portions are canceled out, and the drive shaft can be stably supported by one bearing.

Embodiment 1 FIG.
1 is a longitudinal sectional view schematically showing a configuration of a parallel rotary compressor according to Embodiment 1 of the present invention, and FIG. 2 is a diagram of a first compression mechanism section in the parallel rotary compressor according to Embodiment 1 of the present invention. FIG. 3 is a cross-sectional view for explaining the structure, FIG. 3 is a cross-sectional view for explaining the structure of the second compression mechanism portion in the parallel rotary compressor according to Embodiment 1 of the invention, and FIG. 4 is for Embodiment 1 of the invention. It is a figure explaining the positional relationship of the component of the 1st and 2nd compression mechanism part in the parallel rotary compressor which concerns. FIG. 4 shows a state in which the second compression mechanism portion is projected from the axial direction onto the first compression mechanism portion, the second compression mechanism portion is indicated by a dotted line, and the first and second rolling pistons are omitted. Yes.

  1 to 4, the parallel rotary compressor includes a vertical hermetic shell 1. The electric motor 2 is disposed above the sealed shell 1, and the first and second compression mechanism portions 10 and 20 are disposed below the electric motor 2. The electric motor 2 and the first and second compression mechanisms 10 and 20 are interlocked and connected via the drive shaft 5.

  The electric motor 2 includes a stator 3 formed in a ring shape, and a rotor 4 supported so as to be able to rotate inside the stator 3. One end of the drive shaft 5 is coaxially fixed to the axial center position of the rotor 4, is rotatably supported by the bearing 6, and is disposed in the sealed shell 1.

  The first eccentric portion 7 and the second eccentric portion 8 are provided apart from each other in the axial direction of the drive shaft 5. The first eccentric portion 7 is fixed to the drive shaft 5 with its axis Oa shifted by Δd to one side with respect to the axis O of the drive shaft 5. The second eccentric part 8 is made in the same shape as the first eccentric part 7, and its axis Ob is shifted to the other side by Δd with respect to the axis O of the drive shaft 5 and fixed to the drive shaft 5. Yes. That is, the first eccentric portion 7 and the second eccentric portion 8 are point-symmetric with respect to the axial center O, that is, the positional relationship rotated by 180 ° around the axial center O when viewed from the axial direction. .

  The first cylinder 11 is disposed between the bearing 6 and the partition plate 40. The partition plate 40 has a thickness equivalent to the axial distance between the first eccentric portion 7 and the second eccentric portion 8, and an insertion hole 40a is formed. The second cylinder 21 is sandwiched between the partition plate 40 and the end plate 41 and is disposed coaxially with the first cylinder 11. The drive shaft 5 is rotatably supported by the bearing 6 and penetrates the axial positions of the first cylinder 11, the partition plate 40 and the second cylinder 21. The first eccentric portion 7 is disposed in the first cylinder 11, and the second eccentric portion 8 is disposed in the second cylinder 21. Further, the first rolling piston 12 is fitted into the first eccentric portion 7 so as to be fitted in the first cylinder 11, and the second rolling piston 22 is fitted into the second eccentric portion 8 in a fitted state. It is fitted and disposed in the second cylinder 21.

  The first vane 13 abuts on the outer peripheral surface of the first rolling piston 12 and partitions the low pressure side 14a and the high pressure side 14b in the first compression chamber 14 defined by the first cylinder 11 and the first rolling piston 12. In this manner, the first cylinder 11 is disposed. The first spring 15 is disposed in the first cylinder 11 so as to urge the first vane 13 in a direction in which the first vane 13 is pressed against the outer peripheral surface of the first rolling piston 12. A first suction passage 16 is formed in the first cylinder 11 so as to open to the low pressure side 14 a of the first compression chamber 14 in the vicinity of the first vane 13. Further, the first discharge passage 17 is formed in the first cylinder 11 so as to open to the high pressure side 14 b of the first compression chamber 14 in the vicinity of the first vane 13.

  The second vane 23 abuts on the outer peripheral surface of the second rolling piston 22 and partitions the low pressure side 24a and the high pressure side 24b in the second compression chamber 24 defined by the second cylinder 21 and the second rolling piston 22. In this manner, the second cylinder 21 is disposed. The second spring 25 is disposed in the second cylinder 21 so as to urge the second vane 23 in a direction of pressing the second vane 23 against the outer peripheral surface of the second rolling piston 22. A second suction passage 26 is formed in the second cylinder 21 so as to open to the low pressure side 24 a of the second compression chamber 24 in the vicinity of the second vane 23. Further, the second discharge passage 27 is formed in the second cylinder 21 so as to open to the high pressure side 24 b of the second compression chamber 24 in the vicinity of the second vane 23.

  Here, the first cylinder 11, the first eccentric portion 7, the first rolling piston 12, the second vane 13, the first spring 15, the first suction passage 16, and the first discharge passage 17 are included in the first compression mechanism portion 10. Is configured. The second cylinder 21, the second eccentric portion 8, the second rolling piston 22, the second vane 23, the second spring 25, the second suction passage 26, and the second discharge passage 27 serve as the second compression mechanism portion 20. It is composed.

  The first cylinder 11 is sandwiched between the bearing 6 and the partition plate 40, the openings on both axial sides of the first compression chamber 14 are closed, and the second cylinder 21 is connected to the partition plate 40 and the end plate 41. The openings on both axial sides of the second compression chamber 14 are closed. The first vane 13, the first suction passage 16 and the first discharge passage 17 provided in the first cylinder 11 and the second vane 23, the second suction passage 26 and the second discharge passage provided in the second cylinder 21 are also provided. 27 is a point relationship with respect to the axial center O, that is, a positional relationship rotated by 180 ° around the axial center O when viewed from the axial direction.

  A first suction pipe 30 and a second suction pipe 31 for sucking the refrigerant gas are connected to the first suction passage 16 and the second suction passage 26, respectively, and the discharge pipe 32 for discharging the compressed refrigerant gas is sealed. It is provided in the upper part of the shell 1. The high pressure sides 14b and 24b of the first compression chamber 14 and the second compression chamber 24 communicate with the sealed shell 1 via the first discharge passage 17 and the second discharge passage 27, respectively. The refrigerant gas compressed by the second compression mechanism unit 20 is discharged into the sealed shell 1.

Next, the operation of the parallel rotary compressor configured as described above will be described.
When electric power is supplied to the electric motor 2 and the electric motor 2 is driven, the drive shaft 5 that is cantilevered on the bearing 6 is rotationally driven. Then, the first rolling piston 12 and the second rolling piston 22 rotate eccentrically within the first cylinder 11 and the second cylinder 21. At this time, both end surfaces of the first rolling piston 12 and the second rolling piston 22 are sealed with lubricating oil.
A low-pressure refrigerant gas is introduced into the first compression chamber 14 through the first suction pipe 30 and the first suction passage 16 and is compressed by the first compression mechanism unit 10. The compressed refrigerant gas is discharged into the sealed shell 1 through the first discharge passage 17 and discharged from the discharge pipe 32. Similarly, low-pressure refrigerant gas is introduced into the second compression chamber 24 through the second suction pipe 31 and the second suction passage 26, and is compressed by the second compression mechanism unit 20. The compressed refrigerant gas is discharged into the sealed shell 1 through the second discharge passage 27 and discharged from the discharge pipe 32.

  As described above, the refrigerant gas compression process by the first compression mechanism section 10 includes the suction process in which the refrigerant gas is sucked into the first compression chamber 14 from the first suction passage 16 and the eccentric rotation of the first rolling piston 12. The gas is compressed into a compression process, and the compressed refrigerant gas is discharged from the first discharge passage 17. In a series of compression processes by the first compression mechanism unit 10, a gas load accompanying the compression of the refrigerant gas acts on the drive shaft 5. Similarly, also in a series of compression processes by the second compression mechanism unit 20, a gas load accompanying the compression of the refrigerant gas acts on the drive shaft 5.

Here, the gas load distribution acting on the drive shaft 5 during one rotation of the drive shaft 5 is shown in FIG.
5 that the gas load acting on the drive shaft 5 is a fluctuating load that varies with the rotation of the drive shaft 5. FIG. The first eccentric portion 7, the first vane 13, the first suction passage 16 and the first discharge passage 17 of the first compression mechanism portion 10, the second eccentric portion 8 of the second compression mechanism portion 20, and the second vane. 23, the second suction passage 26 and the second discharge passage 27 are in a positional relationship of being rotated by 180 ° around the axis O as viewed from the axial direction. Therefore, a series of compression processes in the first compression mechanism section 10 and a series of compression processes in the second compression mechanism section are performed at the same timing, and the gas load acting on the drive shaft 5 also increases or decreases at the same timing. Further, the gas load vector acting on the drive shaft 5 by the compression process of the first compression mechanism unit 10 and the gas load vector acting on the drive shaft 5 by the compression process of the second compression mechanism unit 20 are always 180 ° to each other. The opposite direction. Accordingly, the gas load acting on the drive shaft 5 due to the compression process of the first compression mechanism portion 10 and the gas load acting on the drive shaft 5 due to the compression process of the second compression mechanism portion 20 are offset, and a moment is applied to the drive shaft 5. Only will work.

  Next, the gas load and moment acting on the drive shaft 5 will be described based on the model shown in FIG. In FIG. 6, for the coordinate axes, the axial direction of the drive shaft 5 is the Z axis, the direction perpendicular to the paper surface is the Y axis, and the horizontal direction of the paper surface is the X axis. The point a corresponds to the midpoint of the axial length of the bearing 6 in the shaft center of the drive shaft 5, and the point b represents the axial length of the bearing 6 of the first compression mechanism 10 in the shaft center of the drive shaft 5. The position corresponding to the midpoint, the point c is the position corresponding to the midpoint of the axial length of the bearing 6 of the second compression mechanism portion 20 in the axis of the drive shaft 5.

First, the balance formula of the force in the X-axis direction is shown in Formula (1).
R _j = W ₁ −W ₂ (1)
Here, R _j is a bearing reaction force, W ₁ is a gas load acting on the drive shaft 5 from the first compression mechanism portion 10, and W ₂ is a gas load acting on the drive shaft 5 from the second compression mechanism portion 20.

As shown in FIG. 5, the relationship between W ₁ and W ₂ is always expressed by equation (2), and equation (3) is derived from equations (1) and (2).
W ₁ −W ₂ = 0 (2)
R _j = 0 (3)

Here, when the equation (4) is defined, the moment _Mo around the Y axis acting on the point O is expressed by the equation (5).
W = W ₁ = W ₂ (4)
M _o = Wl ₁ (5)

Thus, the moment _Mo shown in the equation (5) acts on the drive shaft 5. Therefore, within the bearing 6, to support the moment M _o, moment M _y around the Y axis in the opposite direction is generated. Moment M _y can be determined Sommerfeld number S, the shaft diameter ratio L / D, the numerical calculation as an input parameter the inclination amount Δε of the drive shaft 5. The Sommerfeld number S is a dimensionless bearing constant expressed by Equation (6).
S = (ηNLD / F) (R / C) ² (6)
Here, η is the viscosity coefficient of the lubricating oil, N is the rotational speed of the drive shaft 5, L is the axial length of the bearing 6, D is the bearing diameter of the bearing 6, R is the bearing radius of the bearing 6, and F is the bearing 6 , C, is a radial clearance between the drive shaft 5 and the bearing 6.

FIG. 7 is a diagram schematically showing the relationship between the bearing and the drive shaft. FIG. 7A is a cross-sectional view orthogonal to the Y axis. FIG. 7B shows a state in which the point where the shaft center of the drive shaft 5 passes through both end faces of the bearing 6 in the axial direction is projected onto a plane orthogonal to the Z axis. That is, Δe shown in FIG. 7B represents the distance in the X-axis direction between the points where the axis of the drive shaft 5 passes through both end surfaces of the bearing 6 in the axial direction. Here, the amount of inclination Δε of the drive shaft 5 is defined as equation (7).
Δε = Δe / C (7)

Hereinafter, a method of calculating the moment _{M y.}
In order to prevent the drive shaft 5 and the bearing 6 from contacting each other, the inclination amount Δε of the drive shaft 5 needs to satisfy the formula (8).
Δε <2 (8)
Here, equation (9) is assumed as a condition where the drive shaft 5 and the bearing 6 do not contact each other.
Δε = 1.8 (9)

Next, the relationship between the Sommerfeld number S and the dimensionless moment M is shown in FIG. The dimensionless moment M is a value obtained by making the sum of the three directions on the coordinate axis dimensionless. The Sommerfeld number S is inversely proportional to the load F acting on the bearing 6 as shown in Equation (6). In order to prevent the load from acting on the bearing 6, strictly speaking, the Sommerfeld number S is infinite, but the dimensionless moment M when the Sommerfeld number S is infinite cannot be calculated. . Here, as shown in FIG. 8, when the Sommerfeld number S increases, the dimensionless moment M converges to a constant value, so the Sommerfeld number S is approximated by Equation (10).
S = 8 (10)

Therefore, equations (9) and (10) are given as fixed values, the shaft diameter ratio L / D is given as an arbitrary value, and the dimensionless moment M is calculated. The results are shown in FIG. 9 that the dimensionless moment M acting on the bearing 6 increases as the shaft diameter ratio L / D increases.
Moment _{M y} can be calculated from the dimensionless moment M, the formula (11).
M _y = (6ηωMRL ² ) (R / C) ² cos γ (11)
Here, ω is the angular velocity of the drive shaft 5, and γ is the moment angle.

The balance equation of the _{M o} represented by the formula (11) _{M y} represented by the formula (5), the shaft diameter ratio L / D is uniquely determined. In this way, the gas loads W ₁ and W ₂ acting on the drive shaft 5 from the first compression mechanism portion 10 and the first compression mechanism portion 20 cancel each other, and the bearing 6 supports only the moment.

  According to the first embodiment, the first eccentric portion 7, the first vane 13, the first suction passage 16 and the first discharge passage 17 of the first compression mechanism portion 10 and the second eccentricity of the second compression mechanism portion 20 are included. Since the core 8, the second vane 23, the second suction passage 26 and the second discharge passage 27 are configured to have a positional relationship of being rotated 180 ° around the axis O as viewed from the axial direction. The drive shaft 5 can be stably supported by one bearing 6. Accordingly, since the drive shaft 5 can be cantilevered, only one bearing 6 is required to support the drive shaft 5, and the parallel rotary compressor that can reduce the axial size of the drive shaft 5 and has little friction loss is realized. Can do.

Embodiment 2. FIG.
FIG. 10 is a longitudinal sectional view of a main part showing the periphery of a compression mechanism part of a parallel rotary compressor according to Embodiment 2 of the present invention.
In FIG. 10, the outer peripheral surface of the second eccentric portion 8A constituting the second compression mechanism portion 20A is processed into a crowning shape.
Other configurations are the same as those in the first embodiment.

  In the second embodiment, since the outer peripheral surface of the second eccentric portion 8A is formed in a crowning shape, the inner peripheral surface of the second rolling piston 22 that is a cylindrical surface is the outer periphery of the second eccentric portion 8A. The surface is brought into line contact with the second eccentric portion 8A. Therefore, when the drive shaft 5 is inclined, the second eccentric portion 8A is inclined while changing the line contact position between the outer peripheral surface and the inner peripheral surface of the second rolling piston 22, and the partition plate 40 and the end plate 41 are changed. The posture of the second rolling piston 22 held between the two is maintained. As a result, generation | occurrence | production per piece with the 2nd rolling piston 22, the partition plate 40, and the end plate 41 is suppressed. Thereby, the abrasion of the 2nd rolling piston 22 resulting from the 2nd rolling piston 22 coming in contact with the partition plate 40 and the end plate 41 is suppressed, and the fall of compression efficiency is suppressed.

Here, the inclination amount of the drive shaft 5 at the extension distance from the bearing 5 becomes larger as the extension distance from the bearing 5 becomes longer, so that the drive shaft 5 is positioned on the front end side in the extension direction from the bearing 6. The rolling piston is easier to hit. Therefore, it is desirable to form at least the outer peripheral surface of the eccentric portion located at the end portion in the extending direction from the bearing 6 of the drive shaft 5 in a crowning shape.
When the drive shaft 5 is excessively inclined, the edge of the outer peripheral surface of the eccentric portion slides on the surface of the end plate 41 or the partition plate 40. Therefore, the eccentric portion is required to have wear resistance and preferably has a hardness of 48 or more on the HRC scale. For example, chrome molybdenum steel that has been quenched and tempered can be used.

  In the second embodiment, the outer peripheral surface of the first eccentric portion is formed as a cylindrical surface. However, in addition to the outer peripheral surface of the second eccentric portion, the outer peripheral surface of the first eccentric portion is also You may form in a crowning shape.

Embodiment 3 FIG.
FIG. 11 is a longitudinal sectional view of a main part showing the periphery of a compression mechanism part of a parallel rotary compressor according to Embodiment 3 of the present invention.
In FIG. 11, a flange portion 42 is integrally formed at one end in the axial direction of the bearing 6A, and an engaged surface 42a on one end side in the axial direction of the flange portion 42 is formed on a flat surface orthogonal to the shaft center of the bearing 6A. ing. The thrust plate 43 is formed integrally with the drive shaft 5A, and the engagement surface 43a on the other end side in the axial direction of the thrust plate 43 is formed on a flat surface orthogonal to the axis of the drive shaft 5A. The drive shaft 5A is rotatably supported by the bearing 6A by bringing the engaging surface 43a of the thrust plate 43 into close contact with the engaged surface 42a of the flange portion 42 in a surface contact state.
Other configurations are the same as those in the first embodiment.

  In the third embodiment, the drive shaft 5A is cantilevered by the bearing 6A with the engagement surface 43a of the thrust plate 43 in close contact with the engaged surface 42a of the flange portion 42, so that the drive shaft 5A is cantilevered. An inclination of 5A is prevented. Accordingly, since the one-side contact of the second rolling plate 22 with the partition plate 40 and the end plate 41 due to the inclination of the drive shaft 5A is avoided, the wear of the second rolling piston 22 is suppressed, and the reduction in compression efficiency is suppressed. .

  In each of the above embodiments, a pair of compression mechanism portions are arranged in parallel in the axial direction of the drive shaft. However, the number of compression mechanism portions arranged in parallel in the axial direction of the drive shaft is limited to one pair. Two or more pairs may be used. In this case, when the pair of compression mechanisms are projected in the axial direction of the drive shaft, the eccentric portion, the vane, the suction passage, and the discharge passage are rotated by 180 ° around the axis of the drive shaft, that is, If it is provided in a point-symmetrical positional relationship with respect to the axis of the drive shaft, it is not necessarily provided adjacent to the drive shaft in the axial direction. For example, when four compression mechanism parts are arranged in parallel in the axial direction of the drive shaft, the compression mechanism parts positioned first and second in the arrangement direction are configured in the above-described point-symmetrical positional relationship, and are arranged in parallel. The third and fourth compression mechanism portions in the direction may be configured in the above-described point-symmetrical positional relationship, or the first and third compression mechanism portions in the juxtaposed direction are in the above-described point symmetry. The second and fourth compression mechanism sections in the juxtaposed direction may be configured in the above point-symmetrical positional relationship.

It is a longitudinal cross-sectional view which shows typically the structure of the parallel rotary compressor which concerns on Embodiment 1 of this invention. It is a cross-sectional view explaining the structure of the 1st compression mechanism part in the parallel rotary compressor which concerns on Embodiment 1 of this invention. It is a cross-sectional view explaining the structure of the 2nd compression mechanism part in the parallel rotary compressor which concerns on Embodiment 1 of this invention. It is a figure explaining the positional relationship of the component of the 1st and 2nd compression mechanism part in the parallel rotary compressor which concerns on Embodiment 1 of this invention. It is a figure which shows the gas load distribution which acts on the drive shaft in the parallel rotary compressor which concerns on Embodiment 1 of this invention. It is a figure which shows the model for calculating the weight which acts on the drive shaft in the parallel rotary compressor which concerns on Embodiment 1 of this invention. It is a figure which shows typically the relationship between the bearing and drive shaft in the parallel rotary compressor which concerns on Embodiment 1 of this invention. It is a figure which shows the relationship between the Sommerfeld number S and the dimensionless moment M. FIG. 4 is a diagram illustrating a relationship between a shaft diameter ratio and a dimensionless moment M. FIG. It is a principal part longitudinal cross-sectional view which shows the surroundings of the compression mechanism part of the parallel rotary compressor which concerns on Embodiment 2 of this invention. It is a principal part longitudinal cross-sectional view which shows the compression mechanism part periphery of the parallel rotary compressor which concerns on Embodiment 3 of this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Sealing shell, 2 Electric motor, 5 Drive shaft, 6, 6A Bearing, 7 1st eccentric part, 8, 8A 2nd eccentric part, 10 1st compression mechanism part, 11 1st cylinder, 12 1st rolling piston, 13 1st vane, 14 1st compression chamber, 14a Low pressure side, 14b High pressure side, 15 1st spring, 16 1st suction passage, 17 1st discharge passage, 20, 20A 2nd compression mechanism part, 21 2nd cylinder, 22 second rolling piston, 23 first vane, 24 first compression chamber, 24a low pressure side, 24b high pressure side, 25 second spring, 26 second suction passage, 27 second discharge passage, 40 partition plate, 41 end plate, 42 Flange part, 42a Engagement surface, 43 Thrust plate, 43a Engagement surface.

Claims (3)

A hermetic shell, an electric motor housed in the hermetic shell, a drive shaft that is driven to rotate by the electric motor, and a shaft coaxial with the drive shaft in the hermetic shell and in parallel in the axial direction of the drive shaft. a parallel rotary compressor that compresses low-pressure refrigerant to high pressure in each of the n pairs of compression mechanism units, wherein n pairs (where n is a positive integer) compression mechanism unit,
Each of the n pairs of compression mechanisms is
A cylinder,
An eccentric portion that is eccentrically disposed on the drive shaft and disposed in the cylinder;
A rolling piston fitted to the eccentric part in an external fitting state;
A vane that abuts on an outer peripheral surface of the rolling piston and partitions a compression chamber defined by the cylinder and the rolling piston into a low pressure side and a high pressure side;
A suction passage formed in the cylinder so as to open to the low pressure side of the compression chamber adjacent to the vane;
A discharge passage formed in the cylinder so as to open to the high pressure side of the compression chamber in the vicinity of the vane,
The cylinder is arranged in parallel in the axial direction of the drive shaft across a partition plate so as to close one opening of the compression chamber;
A bearing is disposed so as to close the other opening of the compression chamber of the cylinder located at one end portion in the axial direction of the drive shaft;
An end plate is disposed so as to close the other opening of the compression chamber of the cylinder located at the other end in the axial direction of the drive shaft;
The drive shaft is cantilevered by the bearing and passes through the cylinder;
The eccentric portion, the vane, the suction passage, and the discharge passage in the compression mechanism portion that forms a pair of the n pairs of compression mechanism portions are 180 around the axis of the drive shaft when viewed from the axial direction of the drive shaft. A parallel rotary compressor characterized in that it is formed at a position shifted by °.   2. The parallel rotary compression according to claim 1, wherein an outer peripheral surface of the eccentric portion disposed in the cylinder located at the other end portion in the axial direction of the drive shaft is processed into a crowning shape. Machine. The flange portion is formed integrally with one end portion in the axial direction of the drive shaft of the bearing, with a flat surface orthogonal to the axis of the drive shaft directed to one side in the axial direction of the drive shaft,
A thrust plate is formed integrally with the drive shaft with a flat surface orthogonal to the axis of the drive shaft facing the other axial direction of the drive shaft;
2. The parallel rotary compressor according to claim 1, wherein the drive shaft is cantilevered by the bearing with the flat surface of the thrust plate in close contact with the flat surface of the flange portion.

Images