JP2016023596A - Hermetic compressor and refrigeration cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hermetic compressor including discharge valves opening or closing discharge holes by two divided partition plates and valve holders supporting the respective discharge valves, capable of ensuring the rigidity of the valve holders even if the partition plates are thin, and capable of being obtained by relatively easy working, and a refrigeration cycle device.SOLUTION: A compressor section of a hermetic compressor comprises: a spindle; a first cylinder including a first cylinder chamber; a first division-partition plate; a second division-partition plate; a second cylinder including a second cylinder chamber; a discharge hole including a sub-bearing, provided in each division-partition plate, and discharging a working fluid compressed in each cylinder chamber; and a discharge valve whose one end portion is attached to each division-partition plate and whose other end portion opens or closes each discharge hole, and a valve holder receiving each discharge valve on a front surface thereof, the front surface of each valve holder being formed such that an attachment portion attached to each division-partition plate is a flat portion and a portion from the flat portion to the other end portion facing each discharge hole is formed to have a predetermined curved cross-section, a rear surface of each valve holder being a flat portion entirely, and the flat portions of the front surface and the rear surface being formed in parallel to each other.SELECTED DRAWING: Figure 4

Description

  Embodiments described herein relate generally to a hermetic compressor and a refrigeration cycle apparatus that includes the hermetic compressor and constitutes a refrigeration cycle.

  In the refrigeration cycle apparatus, a hermetic compressor that houses an electric motor unit and a compression mechanism unit connected to the electric motor unit via a rotating shaft is often used in a hermetic case. The compression mechanism is provided with a pair of upper and lower cylinders via partition plates, compresses the gas refrigerant (working fluid) in the cylinder chamber formed in each cylinder, and discharges the compressed gas refrigerant to the space in the sealed container. To do.

As this hermetic compressor, for example, those described in Patent Document 1 and Patent Document 2 below are known.
In the hermetic compressor described in Patent Document 1, a partition port divided into two and a discharge port are provided in each of the upper bearing (main bearing) and the lower bearing (sub bearing), and the cross-sectional areas of the respective discharge ports are compared. And the amount of lift of the reed valve.

  In the hermetic compressor described in Patent Document 2, an annular groove is provided in the main bearing and the auxiliary bearing, and the shape and size of the annular groove are described. Furthermore, there is a description of providing a discharge valve mechanism on the intermediate partition plate divided into two parts and discharging the gas refrigerant compressed in the corresponding cylinder chamber.

JP2013-83245A W02009 / 145232

  Patent Document 1 does not mention anything about the valve pressing of the reed valve that opens and closes the discharge port of the divided partition plate. Depending on the partition plate and the plate thickness of the reed valve and the valve retainer, the valve retainers come into contact at the time of assembly. Therefore, when the plate thickness of the partition plate is increased, the distance between the crank portions of the rotating shaft is also increased, so that the rotating shaft is easily bent, leading to a decrease in reliability.

The valve retainer shown in Patent Document 2 is formed in a flat shape at one end of the front surface and the back surface attached to the partition plate, and is formed in a predetermined curved shape from this flat shape to the front end of the surface facing the discharge hole. . In another embodiment, the front end of the valve presser is further flattened by cutting the surface (back surface) facing the other valve presser.
In this case, when the plate thickness of the partition plate is reduced, the plate thickness of the valve presser is also reduced, and the rigidity remains uneasy.

  Therefore, in this embodiment, the partition plate is divided into two parts, and includes a discharge valve that opens and closes the discharge hole and a valve presser that supports the discharge valve, and the valve presser ensures rigidity even when the partition plate is thin. It is possible to provide a hermetic compressor that can be obtained by relatively easy processing, and a refrigeration cycle apparatus including the hermetic compressor.

  The hermetic compressor of the present embodiment accommodates an electric motor unit and a compression mechanism unit coupled to the electric motor unit via a rotation shaft in a hermetic container, and the compressor unit is in the axial direction of the rotation shaft. A first bearing having a first cylinder chamber, a first divided partition plate, a second divided partition plate, and a second cylinder chamber having a second cylinder chamber. A first discharge hole that is provided in the first divided partition plate and discharges the working fluid compressed in the first cylinder chamber; and provided in the second divided partition plate. A second discharge hole for discharging the working fluid compressed in the second cylinder chamber, and a first opening having one end attached to the first divided partition plate and opening and closing the first discharge hole at the other end A first valve retainer receiving the discharge valve and the first discharge valve on the surface thereof; A second discharge valve that has one end attached to the partition plate and opens and closes the second discharge hole at the other end, and a second valve retainer that receives the second discharge valve on its surface, On the surfaces of the valve presser and the second valve presser, the first split partition plate and the mounting portion to the second split partition plate form a flat portion, and the first discharge hole and the second discharge from the flat portion. The other end portion facing the hole is formed in a predetermined cross-sectional curved shape, the entire back surface forms a flat portion, and the flat portions on the front and back surfaces are formed in parallel to each other.

  The refrigeration cycle apparatus of this embodiment includes the hermetic compressor according to any one of claims 1 to 5, a condenser, an expansion device, and an evaporator, and constitutes a refrigeration cycle circuit.

The longitudinal cross-sectional view of the hermetic type compressor which concerns on this embodiment, and the refrigerating cycle block diagram of a refrigerating cycle apparatus. The longitudinal cross-sectional view which expanded the compression mechanism part based on the embodiment. The top view of the 2nd division partition plate based on the embodiment. The partial longitudinal cross-sectional view of the partition plate based on the embodiment. The partial longitudinal cross-sectional view of the partition plate which remove | excluded the discharge valve, valve press, and the discharge valve and valve press based on the embodiment. The partial longitudinal cross-sectional view of the partition plate based on the modification of the embodiment.

Hereinafter, the present embodiment will be described with reference to the drawings.
FIG. 1 is a longitudinal sectional view of a hermetic compressor and a refrigeration cycle configuration diagram of a refrigeration cycle apparatus.

  In the figure, reference numeral 1 denotes a hermetic compressor (hereinafter simply referred to as “compressor”), which will be described later. A refrigerant pipe P is connected to the upper end of the compressor 1, and a condenser 2, an expansion valve (expansion device) 3, an evaporator 4 and an accumulator 5 are sequentially provided in the refrigerant pipe P. Further, the refrigerant pipe P branches into two from the accumulator 5 and is connected to the side portion of the compressor 1, and these constitute the refrigeration cycle of the refrigeration cycle apparatus R.

  In the refrigeration cycle apparatus R, the refrigerant, which is a working fluid, circulates while changing phase between a gaseous gas refrigerant and a liquid liquid refrigerant, and is dissipated in the process of phase change from the gas refrigerant to the liquid refrigerant. Heat is absorbed in the process of phase change to the refrigerant, and heating, cooling, heating, cooling, and the like are performed using these heat dissipation and heat absorption.

Next, the compressor 1 will be described.
The compressor 1 includes a hermetic container 10, and an electric motor unit 11 is accommodated in the upper part of the hermetic container 10, and a compression mechanism part 12 is accommodated in the lower part. The electric motor part 11 and the compression mechanism part 12 are They are connected via a rotating shaft 13. Lubricating oil S is stored in the inner bottom portion of the sealed container 10, and the internal space is filled with a high-pressure gas refrigerant compressed by the compression mechanism unit 12.

  A discharge portion 1 a including a hole is provided on the upper surface portion of the hermetic container 10, and a refrigerant pipe P communicating with the condenser 2 is connected thereto. Further, suction portions 1 b and 2 b each having two holes are provided on the lower peripheral wall of the sealed container 10, and a refrigerant pipe P communicating with the accumulator 5 is connected thereto.

  The electric motor unit 11 has a rotor (rotor) 15 fitted and fixed to the rotary shaft 13 and an inner peripheral surface of the outer peripheral surface of the rotor 15 through a narrow gap. It is comprised from the stator (stator) 16 fixed by fitting.

  The rotary shaft 13 is formed with two columnar eccentric parts a and b that protrude toward the outer peripheral side. These eccentric parts a and b are provided at positions displaced by a predetermined dimension along the axial direction of the rotating shaft 13 and at positions displaced by 180 ° along the rotating direction of the rotating shaft 13.

Next, the compression mechanism unit 12 will be described in detail.
FIG. 2 is an enlarged longitudinal sectional view showing the compression mechanism 12.
The compression mechanism unit 12 includes a main bearing 17, a first cylinder 18, a partition plate 20, a second cylinder 22, and a sub bearing 23 along the axial direction of the rotary shaft 13.

  The main bearing 17 is fixed to the first cylinder 18, and the auxiliary bearing 23 is fixed to the first cylinder 18 via the second cylinder 22 and the partition plate 20. The main bearing 17 and the auxiliary bearing 23 pivotally support the rotary shaft 13.

  A first muffler case 25 is fixed to the main bearing 17 and is a hollow case surrounding the main bearing 17, and a first muffler chamber 25 a is formed inside. Further, the first muffler case 25 is provided with a plurality of communication holes c that allow the inside of the first muffler chamber 25a and the space inside the sealed container 10 to communicate. These communication holes c are located above the liquid surface of the lubricating oil S stored in the bottom of the sealed container 10.

A second muffler case 26 is fixed to the auxiliary bearing 23, which is a hollow case surrounding the auxiliary bearing 23, and a second muffler chamber 26a is formed inside.
The first cylinder 18 is fitted and fixed to the inner peripheral wall of the sealed container 10. The inner diameter hole of the first cylinder 18 is closed at the upper end side by the main bearing 17 and closed at the lower end side by the partition plate 20 to form a first cylinder chamber 18A.

The second cylinder 22 is attached to the first cylinder 18 via the partition plate 20. The inner diameter hole of the second cylinder 22 is closed at the upper end side by the partition plate 20 and closed at the lower end side by the auxiliary bearing 23 to form a second cylinder chamber 22A.
The rotary shaft 13 is inserted into the first and second cylinder chambers 18A and 22A, and one eccentric portion a formed on the rotary shaft 13 is located in the first cylinder chamber 18A and formed on the rotary shaft 13. The other eccentric portion b is located in the second cylinder chamber 22A.

A roller 27 is fitted to one eccentric part a, and a roller 28 is fitted to the other eccentric part b. These rollers 27 and 28 roll while a part of the outer peripheral wall abuts against the inner peripheral walls of the first and second cylinder chambers 18A and 22A as the rotary shaft 13 rotates.
Each of the first and second cylinder chambers 18A and 22A is provided with a blade (not shown) so as to be slidable. The tip of the blade is urged by an elastic body such as a spring, and the rollers 27, 28 abuts against the outer peripheral wall.

  A part of the outer peripheral wall of the rollers 27 and 28 is in contact with a part of the inner peripheral wall of the first and second cylinder chambers 18A and 22A, and the tip of the blade 30 is elastically in contact with the outer peripheral wall of the rollers 27 and 28. Thus, the first and second cylinder chambers 18A and 22A are partitioned into two spaces whose volumes change with the rolling of the rollers 27 and 28.

When the motor unit 11 is energized, the rotary shaft 13 rotates and the compression mechanism unit 12 is driven, whereby one space is negatively pressured and gas refrigerant flows. As the rollers 27 and 28 roll, the volume of one space into which the gas refrigerant has flowed gradually decreases, and the gas refrigerant is compressed.
When compressed to a predetermined pressure, the first muffler chamber 25a, the second muffler chamber 26a and the first partition plate muffler chamber 30a, which will be described later in the partition plate 20, and the second partition plate muffler chamber 30b are discharged. After that, it is guided to the space in the sealed container 10.

  The first cylinder 18 is provided with a first suction portion 1b which is a hole for sucking low-pressure gas refrigerant into the first cylinder chamber 18A. The second cylinder 22 is provided with a second suction portion 2b that is a hole for sucking a low-pressure gas refrigerant into the second cylinder chamber 22A. A refrigerant pipe P through which a low-pressure gas refrigerant flows is provided between the first and second suction portions 1 b and 2 b and the accumulator 5.

  The partition plate 20 interposed between the first cylinder 18 and the second cylinder 22 is divided into two along the axial direction of the rotary shaft 13. The first divided partition plate 20a closes the inner diameter hole of the first cylinder 18 together with the main bearing 17, and uses the inner diameter hole as the first cylinder chamber 18A. The second divided partition plate 20b closes the inner diameter hole of the second cylinder 22 together with the auxiliary bearing 23, and uses the inner diameter hole as the second cylinder chamber 22A.

Next, a structure for guiding the gas refrigerant compressed in the first cylinder chamber 18A and the second cylinder chamber 22A to the space in the sealed container 10 will be described.
A flange portion 17a of the main bearing 17 is provided with a main bearing discharge hole 32 for discharging the gas refrigerant compressed in the first cylinder chamber 18A to the first muffler chamber 25a. The main bearing discharge hole 32 communicates with the first cylinder chamber 18A at a predetermined timing accompanying the rotation of the rotary shaft 13.

  Further, the flange portion 17 a of the main bearing 17 is provided with a main bearing discharge valve 33 that opens and closes the main bearing discharge hole 32 and a main bearing valve presser 34 that regulates the maximum opening of the main bearing discharge valve 33. A notch groove 35 is formed in a portion of the first cylinder 18 facing the main bearing discharge hole 32.

  The first divided partition plate 20a constituting one of the two divided partition plates 20 discharges the gas refrigerant compressed in the first cylinder chamber 18A to the first partition plate muffler chamber 30a. A discharge hole 36 is formed. The first discharge hole 36 communicates with the first cylinder chamber 18 </ b> A at a predetermined timing associated with the rotation of the rotary shaft 13. The first divided partition plate 20a is provided with a first discharge valve 37 that opens and closes the first discharge hole 36, and a first valve presser 38 that regulates the maximum opening degree of the first discharge valve 37. It is done.

  The flange portion 23a of the sub bearing 23 is provided with a sub bearing discharge hole 40 for discharging the gas refrigerant compressed in the second cylinder chamber 22A to the second muffler chamber 26a. The auxiliary bearing discharge hole 40 communicates with the second cylinder chamber 22A at a predetermined timing accompanying the rotation of the rotary shaft 13.

  Further, the flange portion 23 a of the auxiliary bearing 23 is provided with an auxiliary bearing discharge valve 41 that opens and closes the auxiliary bearing discharge hole 40, and an auxiliary bearing valve presser 42 that regulates the maximum opening degree of the auxiliary bearing discharge valve 41. A notch groove 43 is formed in a portion of the second cylinder 22 facing the auxiliary bearing discharge hole 40.

  A gas refrigerant compressed in the second cylinder chamber 22A is discharged to the second partition plate muffler chamber 30b in the second divided partition plate 20b constituting the other of the two divided partition plates 20. The discharge hole 45 is formed. The second discharge hole 45 communicates with the second cylinder chamber 22A at a predetermined timing accompanying the rotation of the rotary shaft 13. The second divided partition plate 20b is provided with a second discharge valve 46 that opens and closes the second discharge hole 45, and a second valve presser 47 that restricts the maximum opening of the second discharge valve 46. It is done.

  A first muffler chamber 25 a in a first muffler case 25 attached to the main bearing 17, first and second partition plate muffler chambers 30 a and 30 b provided in the partition plate 20 divided into two, and a sub-bearing 23 are provided. The second muffler chamber 26a in the second muffler case 26 to be communicated with each other.

  If it demonstrates, the 1st discharge flow path 48 will be formed through the flange part 17a of the main bearing 17, the 1st cylinder 18, and the 1st division | segmentation partition plate 20a. Further, a second discharge passage 49 is formed through the flange portion 23 a of the sub bearing 23 and the second cylinder 22. The first and second discharge channels 48 and 49 are in communication with each other, and therefore the first muffler chamber 25a, the first and second partition plate muffler chambers 30a and 30b, and the second muffler chamber 26a are in communication. .

  In such a configuration, when the electric motor unit 11 is energized and the rotary shaft 13 is rotationally driven, the low-pressure gas refrigerant that has passed through the accumulator 5 is supplied from the suction parts 1b and 2b through the refrigerant pipe P to the first. The gas refrigerant sucked into the second cylinder chambers 18A and 22A is compressed.

The gas refrigerant compressed in the first cylinder chamber 18A is discharged from the main bearing discharge hole 32 and the first discharge hole 36, and passes through the compressed gas refrigerant discharged from the first cylinder chamber 18A. The total area of the discharge holes 32 and 36 is increased.
For this reason, even when the amount of the gas refrigerant discharged from the first cylinder chamber 18A increases, the pressure loss when the compressed gas refrigerant passes through the main bearing discharge hole 32 and the first discharge hole 36. Can be suppressed, and the performance of the hermetic compressor 1 can be improved.

The gas refrigerant compressed in the second cylinder chamber 22A is discharged from the auxiliary bearing discharge hole 40 and the second discharge hole 45, and the compressed gas refrigerant is discharged from the second cylinder chamber 22A. The total area of the discharge holes 40 and 45 is increased.
For this reason, even when the amount of the gas refrigerant discharged from the second cylinder chamber 22A increases, the pressure loss when the compressed gas refrigerant passes through the auxiliary bearing discharge hole 40 and the second discharge hole 45. The compression performance of the hermetic compressor 1 can be improved.

  Further, by reducing the volume of the first and second partition plate muffler chambers 30a and 30b, the partition plate 20 can be thinned, and thus the interval between the main bearing 17 and the sub bearing 23 can be reduced. it can. By reducing the distance between the main bearing 17 and the sub-bearing 23, the rotating shaft 13 can be prevented from coming into contact with the main bearing 17 and the sub-bearing 23 and the bending of the rotating shaft 13 can be reliably prevented.

  A notch groove 35 is provided in a portion of the first cylinder 18 facing the main bearing discharge hole 32, and a notch groove 43 is provided in a portion of the second cylinder 22 facing the auxiliary bearing discharge hole 40. Therefore, the gas refrigerant can be smoothly discharged from the main bearing discharge hole 32 and the sub-bearing discharge hole 40 in the final stage of the gas refrigerant compression process.

  The gas refrigerant in the first muffler chamber 25 a is guided to the space in the sealed container 10 from the communication hole c provided in the first muffler case 25. Since this communication hole c is located above the liquid level of the lubricating oil S stored in the sealed container 10, the lubricating oil by the gas refrigerant guided to the space in the sealed container 10 from the communication hole c is provided. Forming and forming lubricant oil can be suppressed from being discharged to the outside of the sealed container 10 together with the gas refrigerant.

  Since the partition plate 20 is formed by connecting two members of the first divided partition plate 20a and the second divided partition plate 20b, the first and second partition plate muffler chambers 30a and 30b are formed. In addition, the first and second valve pressers 38 and 47 can be easily provided.

FIG. 3 is a plan view of the second divided partition plate 20b. Here, the first divided partition plate 20a (not shown) has the same configuration, and the description of the second divided partition plate 20b is applied to omit the new description.
FIG. 4 is a view in which the first divided partition plate 20a is combined with the second divided partition plate 20b shown in FIG. 3, and the portion along the line AA in FIG.

  In the second divided partition plate 20 b shown in FIG. 3, the second discharge valve 46 overlaps the second valve presser 47, and the second discharge valve 46 opens and closes the second discharge hole 45. The second divided partition plate 20b is provided with a groove-shaped second partition plate muffler chamber 30b whose upper part is opened from the periphery of the second discharge hole 45 to the second discharge flow path 49 described above. It has been.

  As shown in FIG. 4, the first divided partition plate 20a also has a groove-shaped first partition whose lower part is opened from the periphery of the first discharge hole 36 to the first discharge channel 48 described above. A plate muffler chamber 30b is provided. The first and second partition plate muffler chambers 30a and 30b are provided at the same position of the first and second partition partition plates 20a and 20b, and the space portions thereof face each other to form the same space.

  As described above, the first divided partition plate 20a is formed with the first discharge hole 36 for discharging the gas refrigerant compressed in the first cylinder chamber 18A. Further, the first divided partition plate 20 a is provided with a first discharge valve 37 that opens and closes the first discharge hole 36 and a first valve presser 38 that regulates the maximum opening degree of the first discharge valve 37. It is done.

  One end of the first discharge valve 37 and the first valve presser 38 is fixedly attached to the first divided partition plate 20a via a mounting screw 52a that is a fixture, and the other end of the first valve presser 38 is Opposite the first discharge hole 36.

  A second discharge hole 45 for discharging the gas refrigerant compressed in the second cylinder chamber 22A is formed in the second divided partition plate 20b. Further, the second divided partition plate 20b is provided with a second discharge valve 46 that opens and closes the second discharge hole 45, and a second valve presser 47 that restricts the maximum opening of the second discharge valve 46. It is done.

One end of the second discharge valve 46 and the second valve presser 47 is fixedly attached to the second divided partition plate 47 via a mounting screw 52b as a fixture, and the other end of the second valve presser 47 is Opposing to the second discharge hole 45.
The first discharge hole 36 and the second discharge hole 45 are provided at positions facing each other. The mounting screw 52a for attaching the first discharge valve 37 and the first valve presser 38, the second discharge valve 46, and the second discharge valve 46 are provided. Two valve pressers 47 are provided at positions facing the mounting screws 52b.

  Therefore, the first valve presser 38 and the second valve presser 47 are provided at the same position and facing each other. However, the first valve retainer 38 and the second valve retainer 47 are attached to each other with a predetermined gap γ, and are not in close contact with each other.

  5A is a longitudinal sectional view of the first discharge valve 37, FIG. 5B is a longitudinal sectional view of the first valve presser 38, and FIG. 5C is a first and second divided partition plate 20a. , 20b. Here, since the second discharge valve 46 and the second valve presser 47 (not shown) have the same configuration as the first discharge valve 37 and the first valve presser 38, the same description is applied and a new description is omitted. To do.

  The first discharge valve 37 shown in FIG. 5A is made of a thin leaf spring plate having a predetermined plate thickness α, and has a substantially strip shape with both ends being semicircular in plan view. An attachment hole 53a through which the attachment screw 52a is inserted is provided at one end portion, and the first discharge hole 36 can be opened and closed at the other end portion.

  The first valve retainer 38 shown in FIG. 5 (B) has a predetermined thickness t at one end, and is provided with a screw hole 54a for screwing the mounting screw 52a. A surface portion of a predetermined length L including the screw hole 53a from one end of the first valve presser 38 is a surface flat portion 55 formed in a highly accurate flat shape. From the flat surface portion 55 to the tip of the first valve presser 38, a curved portion 56 having a curved cross section is formed.

The entire back surface of the first valve presser 38 is a back surface flat portion 57 that is formed in a highly accurate flat shape. The front surface flat part 55 and the back surface flat part 57 are parallel to each other, and no inclination should occur in either one of them.
As described above, the first and second divided partition plates 20a and 20b shown in FIG. 5C are provided with the mounting holes 58a and 58b through which the mounting screws 52a and 52b are inserted facing each other at the same position.

  As shown in FIG. 4, the mounting screws 52a and 52b are provided in the first and second discharge valves 37 and 46 through mounting holes 58a and 58b provided in the first and second divided partition plates 20a and 20b. The mounting holes 53a and 53b are inserted into the screw holes 54a and 54b provided in the first and second valve pressers 38 and 47, respectively.

  The heads f of the mounting screws 52a and 52b protrude from the first and second divided partition plates 20a and 20b, but the threaded portion g has screw holes 53a and 53a of the first and second valve holders 38 and 47, respectively. It is necessary to use the thing of the length within the range of the length of 53b, and must not protrude from the back surface of the 1st, 2nd valve holders 38 and 47. Thus, it is possible to avoid setting the gap γ between the first and second divided partition plates 20a and 20b.

  The first discharge hole 36 and the second discharge hole 45 that are mounted with a predetermined distance from the mounting holes 58a and 58b are provided opposite to each other at the same position as described above, and have the same diameter φd. Is set.

When the thickness of the first and second divided partition plates 20a and 20b is H, the height of the space obtained by subtracting the thickness e of the mounting portion of the first discharge valve 37 and the first valve presser 38 is h. And
From the above conditions, settings are made so as to satisfy the following expressions (1) and (2).
h / (t + α) ≧ 1 (1)
γ / d ≦ 0.07 (2)
That is, by satisfying the expression (1), the first and second valve pressers 38 and 47 can be accommodated within the thicknesses of the first and second divided partition plates 20a and 20b.

  Further, the surfaces of the first and second valve pressers 38 and 47 are formed in a flat shape with a predetermined length L from one end, and the entire back surface is formed in a flat shape parallel to the flat surface portion. . Therefore, the plate thickness of the first and second valve pressers 38 and 47 can be increased to increase the rigidity, and the rigidity anxiety at the time of over-compression or the like is eliminated.

  On the other hand, the first valve retainer 38 and the second valve retainer 47 can increase the plate thickness on one end side, but the plate thickness on the distal end side becomes thinner than the one end side. Therefore, it is ideal that γ = 0 be brought into contact with each other at the time of assembly. However, from the manufacturing tolerance of these valve holders 38 and 47 and the condition of assembly error with respect to the first and second divided partition plates 20a and 20b. Have difficulty.

Therefore, by satisfying the expression (2), one discharge valve (for example) 38 deforms one end portion to open the discharge hole 36 and is received by the opposing valve press 38, and the received valve press 38 is When bending deformation occurs, contact with the opposing valve presser 47 prevents excessive bending deformation and improves reliability.
If a gap γ that exceeds the numerical value (0.07) regulated by equation (2) is formed, the deflection of the valve retainer 38 when receiving the deformed discharge valve 37 becomes large, resulting in a lack of reliability. .

FIG. 6 is a diagram illustrating a modification of the present embodiment.
Here, attachment rivets 152a and 152b are used as attachments. Since the components and conditions other than the fixture are the same as those described above, new descriptions are omitted.

  The first and second valve pressers 38 and 47 are provided with mounting holes 154a and 154b in place of the screw holes 54a and 54b described above. Then, recesses 155a and 155b having larger diameters than the mounting holes 154a and 154b are provided from the back surfaces of the first and second valve pressers 38 and 47 to the mounting holes 154a and 154b.

The heads m of the mounting rivets 152a and 152b protrude from the first and second divided partition plates 20a and 20b, but the pressing end n of the mounting rivets 152a and 152b is the first and second divided partition plates 20a and 20b. It is accommodated in recesses 155a and 155b provided in 20b.
That is, the pressing end n of the mounting rivets 152a and 152b does not protrude from the back surfaces of the first and second divided partition plates 20a and 20b, and therefore, the first and second divided partition plates 20a and 20b are mutually connected. This does not obstruct the setting of the gap γ.

In addition, although the said embodiment demonstrated what provided the main bearing discharge hole 32 and the subbearing discharge hole 40, the main bearing discharge hole 32 and the subbearing discharge hole 40 are not an essential structure.
As mentioned above, although this embodiment was described, the above-mentioned embodiment is shown as an example and does not intend limiting the range of embodiment. The novel embodiment can be implemented in various other forms, and various omissions, substitutions, and changes can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the claims and the equivalents thereof.

  DESCRIPTION OF SYMBOLS 10 ... Sealed container, 11 ... Electric motor part, 13 ... Rotating shaft, 12 ... Compression mechanism part, 17 ... Main bearing, 18A ... 1st cylinder chamber, 18 ... 1st cylinder, 20a ... 1st division | segmentation partition plate, 20b ... 2nd division partition plate, 22A ... 2nd cylinder chamber, 22 ... 2nd cylinder, 23 ... Sub bearing, 36 ... 1st discharge hole, 45 ... 2nd discharge hole, 37 ... 1st Discharge valve, 38 ... first valve retainer, 46 ... second discharge valve, 47 ... second valve retainer, 55 ... surface flat portion, 57 ... back surface flat portion, 56 ... curved portion, 155a, 155b ... concave

Claims (4)

In an airtight container, an electric motor part and a compression mechanism part connected to the electric motor part via a rotating shaft are accommodated,
The compressor section includes a main bearing provided in order along the axial direction of the rotary shaft, a first cylinder having a first cylinder chamber, a first divided partition plate, and a second divided partition plate. And a second cylinder having a second cylinder chamber, and a secondary bearing,
A first discharge hole provided in the first divided partition plate for discharging a working fluid compressed in the first cylinder chamber; and provided in the second divided partition plate, the second cylinder chamber. A second discharge hole for discharging the working fluid compressed by
A first discharge valve having one end attached to the first divided partition plate and opening and closing the first discharge hole at the other end, and a first valve presser receiving the first discharge valve on the surface thereof When,
A second discharge valve having one end attached to the second divided partition plate and opening and closing the second discharge hole at the other end, and a second valve presser receiving the second discharge valve on its surface When,
Comprising
The surfaces of the first valve retainer and the second valve retainer have flat portions formed by attaching the first divided partition plate and the second divided partition plate to the first divided partition plate. The discharge hole and the other end opposite to the second discharge hole are formed to have a predetermined cross-sectional curved shape, the entire back surface forms a flat portion, and the flat portions on the front and back surfaces are formed in parallel to each other. A hermetic compressor characterized by An attachment for attaching the first discharge valve and the first valve retainer to the first divided partition plate, and an attachment for attaching the second discharge valve and the second valve retainer to the second divided partition plate 2. The hermetic compressor according to claim 1, wherein the components are not protruded from the back surface of the first valve presser and the back surface of the second valve presser, respectively. The plate thickness of the first divided partition plate and the second divided partition plate is H, the plate thickness of the first discharge valve and the second discharge valve is α, the first discharge hole and the second The diameters of the discharge holes are d, the thicknesses of the first valve presser and the second valve presser are t, and the thickness H of the first and second divided partition plates is used for the first and second discharges. When the height of the space obtained by subtracting the thickness of the valve mounting portion is h, and the gap between the first valve presser and the second valve presser is γ, the following formulas (1) and (2) are satisfied. The hermetic compressor according to any one of claims 1 and 2, wherein the hermetic compressor is provided.
h / (t + α) ≧ 1 (1)
γ / d ≦ 0.07 (2) A refrigeration cycle apparatus comprising the hermetic compressor according to any one of claims 1 to 3, a condenser, an expansion device, and an evaporator, and constituting a refrigeration cycle circuit.

Images