JP4488104B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor that compresses a refrigerant.

  In the compressor described in Patent Document 1, a piston in which a roller and a blade are integrally formed is arranged inside a cylinder chamber formed inside the cylinder, and the piston makes the cylinder chamber a suction chamber (low-pressure chamber). Chamber) and discharge chamber (high pressure chamber). Then, the roller moves along the side wall surface while contacting the side wall surface of the cylinder chamber, whereby the volume of the discharge chamber changes and the refrigerant in the discharge chamber is compressed.

JP 2004-124948 A

  Here, in the compressor described in Patent Document 1, in order to prevent the movement of the piston from being obstructed by contact with the upper and lower wall surfaces of the cylinder chamber, the piston (roller and blade) is more than the cylinder chamber. The height is low. Since the roller is lower than the cylinder chamber, the lubricating oil flowing inside the roller flows into the low-pressure chamber through the gap between the roller and the upper and lower wall surfaces of the cylinder chamber. However, when the amount of lubricating oil flowing into the low pressure chamber from the inside of the roller increases, the temperature of the refrigerant in the low pressure chamber increases due to this lubricating oil, and the performance of the compressor decreases.

  Further, since the blade is lower in height than the cylinder chamber, the lubricating oil flows from the high pressure chamber into the low pressure chamber through a gap between the blade and the upper and lower wall surfaces of the cylinder chamber. Here, since the refrigerant is compressed in the high-pressure chamber, the temperature of the high-pressure chamber is high, and the temperature of the lubricating oil in the high-pressure chamber is also high. Therefore, when the amount of lubricating oil flowing from the high pressure chamber into the low pressure chamber increases, the temperature of the refrigerant in the low pressure chamber increases, and the performance of the compressor decreases.

  An object of the present invention is to provide a compressor in which the amount of the lubricating oil flowing into the low pressure chamber is small and the performance does not deteriorate.

A compressor according to a first aspect of the present invention is disposed in a sealed space, is provided with a cylinder provided with a cylinder chamber therein, and is disposed within the cylinder chamber, the outer peripheral surface of which is the side of the cylinder chamber. A refrigerant is introduced from the outside, which moves along the side wall surface so as to abut against the wall surface, compresses the refrigerant in the cylinder chamber, and discharges the compressed refrigerant to the sealed space. An annular roller that is divided into a low-pressure chamber and changes the volume of the high-pressure chamber and the low-pressure chamber, and is disposed inside the cylinder chamber. The cylinder chamber together with the roller is divided into the high-pressure chamber and the low-pressure chamber. blades and, said blade comprises a single spring which presses against the roller, the roller has a plurality of rollers constituent members are laminated in the axial direction of the cylinder to divide the bets Thus with is configured, the blade is characterized in that it is constituted by a plurality of blade components is pressed toward the roller by the one spring while being stacked in the axial direction of the cylinder.

  In this compressor, since the blade is constituted by a plurality of laminated blade constituent members, an oil film of lubricating oil is formed between the blade constituent members and a gap is formed between the blade constituent members. In the cylinder chamber, the size of the gap between the wall surfaces on both sides in the axial direction of the cylinder and the size of the gap between the blade constituent members are the same as in the conventional case where the blade is configured by one member. This is smaller than the size of the gap between the blade and the wall surfaces on both sides of the cylinder chamber in the axial direction of the cylinder.

  Therefore, the sum of the size of the gap between the blade constituent member and the wall surfaces on both sides of the cylinder chamber in the cylinder chamber and the size of the gap between the blade constituent members is one member as in the prior art. The amount of lubricating oil flowing from the high-pressure chamber to the low-pressure chamber can be reduced even if it is the same as the sum of the sizes of the gaps between the blades and the wall surfaces on both sides of the cylinder chamber in the axial direction in the cylinder chamber. .

  Alternatively, when the amount of lubricating oil flowing from the high-pressure chamber to the low-pressure chamber is approximately the same as the conventional amount, the size of the gap between the blade constituent member and the upper and lower wall surfaces of the cylinder chamber, and the gap between the blade constituent members Can be made larger than the sum of the sizes of the gaps between the blade and the wall surfaces on both sides of the cylinder chamber in the axial direction of the cylinder when the blade is constituted by one member as in the prior art, It is possible to reliably prevent the blade constituent member from coming into contact with the wall surfaces on both sides of the cylinder chamber in the axial direction of the cylinder.

  Furthermore, when the blade is constituted by a single member, there is a risk that heat will be trapped in the central portion in the height direction of the blade and seizure may occur. Since the blades are formed by laminating the constituent members, the lubricating oil flows through the gaps between the blade constituent members, and the above-described seizure hardly occurs.

  In this compressor, the distance between the blade constituent member and the wall surfaces on both sides in the axial direction of the cylinder in the cylinder chamber is shortened by an amount corresponding to the gap between the blade constituent members. When the wall surfaces on both sides in the cylinder axial direction in the cylinder chamber approach the blade component due to the difference in the linear expansion deformation amount, the oil film is crushed and the gap between the blade components is reduced. Thus, the blade does not easily come into contact with the wall surfaces on both sides of the cylinder chamber in the axial direction of the cylinder.

In this compressor, since the roller is constituted by a plurality of roller constituent members stacked in the axial direction of the cylinder, an oil film of lubricating oil is formed between the roller constituent members while the compressor is driven, A gap is formed between the roller constituent members, and the size of the gap between the roller constituent members and the wall surfaces on both sides of the cylinder chamber in the axial direction of the cylinder and the size of the gap between the roller constituent members are conventionally Thus, the size of the gap between the roller when the roller is made of one member and the wall surfaces on both sides of the cylinder chamber in the axial direction of the cylinder is smaller. On the other hand, from the viewpoint of hydrodynamics, it is known that the amount of liquid flowing in the gap is smaller as the number of gaps is larger and the size of one gap is smaller when the total gap size is the same. .
Therefore, the sum of the size of the gap between the roller constituent member and the wall surfaces on both sides of the cylinder chamber in the cylinder chamber and the size of the gap between the roller constituent members is one member as in the prior art. Even if it is the same as the sum of the sizes of the gaps between the rollers and the wall surfaces on both sides of the cylinder chamber in the axial direction in the cylinder chamber, the amount of lubricating oil flowing into the low pressure chamber can be reduced.
Alternatively, in the case where the amount of lubricating oil flowing into the low-pressure chamber is approximately the same as the conventional amount, the size of the gap between the roller constituent member and the wall surfaces on both sides of the cylinder chamber in the axial direction of the cylinder, and the roller constituent member The total size of the gaps between the rollers is larger than the total size of the gaps between the rollers and the wall surfaces on both sides of the cylinder chamber in the axial direction of the cylinder when the rollers are configured by one member as in the prior art. It is possible to reliably prevent the roller constituent members from coming into contact with the wall surfaces on both sides of the cylinder chamber in the axial direction of the cylinder.
In this compressor, the distance between the roller constituent member and the wall surfaces on both sides of the cylinder chamber in the axial direction of the cylinder is shortened by an amount corresponding to the gap between the roller constituent member. When the wall surfaces on both sides in the cylinder axial direction in the cylinder chamber approach the roller component due to the difference in linear expansion deformation amount, the oil film is crushed and the gap between the roller components is reduced. Thus, the roller does not easily come into contact with the wall surfaces on both sides of the cylinder chamber in the axial direction of the cylinder.

  As described above, according to the present invention, the following effects can be obtained.

  In the first invention, the total size of the gap between the blade constituent member and the wall surfaces on both sides of the cylinder chamber in the cylinder chamber in the axial direction of the cylinder and the size of the gap between the blade constituent members is The amount of lubricating oil flowing from the high-pressure chamber to the low-pressure chamber is reduced even if it is the same as the total size of the gap between the blade and the wall surfaces on both sides of the cylinder chamber in the axial direction in the cylinder chamber can do.

  Alternatively, in the first invention, when the amount of lubricating oil flowing from the high-pressure chamber into the low-pressure chamber is approximately the same as the conventional amount, the gap between the blade constituent member and the wall surfaces on both sides of the cylinder chamber in the axial direction of the cylinder And the total size of the gaps between the blade constituent members are the gaps between the blades and the wall surfaces on both sides of the cylinder chamber in the axial direction of the cylinder when the blade is constituted by one member as in the prior art. It can be made larger than the total size, and it is possible to reliably prevent the blade constituent member from coming into contact with the wall surfaces on both sides of the cylinder chamber in the axial direction of the cylinder.

Furthermore, the blade when is constituted by a single member, although there is a possibility that seizure would heat is muffled in a central portion about the height direction of the blade occurs, in the first invention, a plurality of Since the blades are formed by laminating the blade constituent members, the lubricating oil flows in the gaps between the blade constituent members, and the above-described seizure hardly occurs.

In the first invention, the total size of the gap between the roller constituent member and the wall surfaces on both sides in the cylinder chamber in the cylinder chamber and the size of the gap between the roller constituent members is The amount of lubricating oil flowing into the low pressure chamber is reduced even when the size of the gap between the roller and the wall surface on both sides of the cylinder chamber in the axial direction of the cylinder is the same as the sum of the sizes of the rollers when the roller is constituted by one member. be able to.

Alternatively, in the first invention , when the amount of lubricating oil flowing into the low-pressure chamber is set to the same level as the conventional one, the size of the gap between the roller constituent member and the wall surfaces on both sides of the cylinder chamber in the axial direction of the cylinder , And the total size of the gap between the roller constituent members is the size of the gap between the roller and the wall surface on both sides of the cylinder chamber in the axial direction of the cylinder when the roller is constituted by one member as in the prior art. It can be made larger than the total, and it is possible to reliably prevent the roller constituent members from contacting the wall surfaces on both sides of the cylinder chamber in the axial direction of the cylinder.

It is a schematic block diagram of the compressor which concerns on the reference example 1 of this invention. It is a top view which shows the structure and operation | movement of these cylinders and pistons of FIG. 2 is a perspective view of the piston. FIG. 4 is a cross-sectional view taken along line IV-IV in FIG. 2, where (a) shows a reference example 1 and (b) shows a conventional one. It is the VV sectional view taken on the line of FIG. 2, (a) is based on the reference example 1, (b) has shown the conventional one. It is a figure which shows oil film reaction force generated between a piston and the eccentric part of a shaft, and the distribution of the magnitude | size, (a) is a state without a clearance gap between two piston structural members, (b) is two. The state which the clearance gap was made between piston structural members is shown. FIG. 4 is a diagram corresponding to FIG. 3 of Reference Example 2. FIG. 3 is a view corresponding to FIG. 2 of the embodiment of the present invention. FIG. 4 is a diagram corresponding to FIG. 3 of the embodiment of the present invention. FIG. 6 is a diagram corresponding to FIG. 3 of Reference Example 3. FIG. 6 is a diagram corresponding to FIG. 3 of Reference Example 4 .

  Hereinafter, reference examples and embodiments of a compressor according to the present invention will be described with reference to the drawings.

  FIG. 1 is a schematic configuration diagram of a compressor according to Reference Example 1. The compressor 1 is, for example, a compressor used in an air conditioner such as an air conditioner. The compressor 1 compresses the refrigerant from which moisture has been removed and is introduced from the accumulator 2, and is discharged from a discharge passage 25 disposed at the upper end portion thereof. Discharge the compressed refrigerant. As shown in FIG. 1, the compressor 1 includes a casing 11, a motor 12, and a compression mechanism 13.

  The casing 11 includes a body 21, a top 22 and a bottom 23. The trunk | drum 21 is a substantially cylindrical member extended in the up-down direction, The upper and lower ends are opening. In addition, two connection ports 24 are formed on the side surface of the body 21 along the vertical direction to which the discharge pipe 2a for discharging the refrigerant of the accumulator 2 is connected at the lower right end. The top 22 is a member that closes the opening at the upper end of the body 21. The top 22 is provided with the discharge channel 25 described above. The bottom 23 is a member that closes the opening at the lower end of the body 21. In the casing 11, a sealed space 26 surrounded by the body 21, the top 22, and the bottom 23 is formed.

  The motor 12 is disposed in the sealed space 26 and has a stator 31 and a rotor 32. The stator 31 is fixed to the inner wall surface of the body 21. The rotor 32 is disposed on the radially inner side of the stator 31, and an upper end portion of a shaft 60 extending in the vertical direction is fixed to a substantially central portion thereof. In the motor 12, the rotor rotates together with the shaft 60 by the magnetic force generated between the stator 31 and the rotor 32. Note that the configuration of the stator 31 and the rotor 32 is the same as that of a conventional motor, and thus detailed description thereof is omitted here.

  The compression mechanism 13 is disposed in the sealed space 26 and is located below the motor 12. The compression mechanism 13 is a so-called rotary type compression mechanism in which a roller and a blade are integrally formed. As shown in FIG. 1, the compression mechanism 13 includes a cylinder 61, a piston 62, a front head 63, a middle plate 64, and a rear head 65. is doing. FIG. 2 is a plan view showing the configuration of the cylinder 61 and the piston 62 of FIG. 1 and their operations. FIG. 3 is a perspective view of the piston 62 of FIG. 4 is a sectional view taken along line IV-IV in FIG. 5 is a cross-sectional view taken along line VV in FIG.

  As shown in FIGS. 1 to 5, the two cylinders 61 are arranged along the vertical direction of FIG. 1, and a substantially circular cylinder chamber in a plan view that penetrates the cylinder 61 in the vertical direction at a substantially central portion thereof. 71 is formed. The upper and lower openings of the cylinder chamber 71 of the cylinder 61 disposed above are closed by the front head 63 and the middle plate 64, respectively. On the other hand, the openings at the upper and lower ends of the cylinder chamber 71 of the cylinder 61 disposed below are closed by the middle plate 64 and the rear head 65, respectively.

  The cylinder 61 accommodates blade constituent portions 81b and 82b, which will be described later, of the piston 62, which communicate with the cylinder chamber 71 and extend in the vertical direction of FIG. 2 above the cylinder chamber 71 in FIG. A blade storage chamber 75 is formed.

  Further, the cylinder 61 is formed with an introduction flow path 72 extending rightward in FIG. 1 from the introduction port 71b formed in the right side portion of the side wall surface 71a of the cylinder chamber 71 in FIG. The discharge pipe 2 a of the accumulator 2 connected to is connected to the introduction flow path 72. Thereby, the refrigerant introduced into the compressor 1 from the accumulator 2 flows into the cylinder chamber 71 (more specifically, a low-pressure chamber 71c described later) from the introduction port 71b via the introduction flow path 72.

  The piston 62 is configured by stacking two piston constituent members 81 and 82 in the vertical direction (the axial direction of the cylinder 61), and is disposed inside the two cylinder chambers 71, respectively. The piston component 81 includes a roller component 81a and a blade component 81b. The piston component 82 includes a roller component 82a and a blade component 82b. The piston component 81 and the piston component 82 are the same. It has the shape of

  The roller constituting portions 81 a and 82 a are both formed in an annular shape in a plan view, and are stacked inside each other and disposed inside the cylinder chamber 71. The blade constituting portions 81b and 82b are integrally formed with the roller constituting portions 81a and 82a, respectively, and extend upward in the drawing from the upper end portions in FIG. 2 of the outer peripheral surfaces 81c and 82c of the roller constituting portions 81a and 82a. Yes.

  Further, the blade constituting portions 81b and 82b are stacked on each other, and the lower end portion in FIG. 2 connected to the roller constituting portions 81a and 82a is disposed in the cylinder chamber 71 together with the roller constituting portions 81a and 82a. The upper end portion is disposed in the blade storage chamber 75 and is slidably supported by a bush 73 disposed in the blade storage chamber 75.

  The roller component 81a and the roller component 82a stacked on each other correspond to the roller according to this reference example, and the blade component 81b and the blade component 82b stacked on each other are referred to in this reference. It corresponds to the blade according to the example. That is, in this reference example, the roller and the blade are integrally formed. Therefore, as will be described later, when the piston 62 moves, the roller and the blade do not slide and burn-in does not occur.

  The shaft 60 described above penetrates the roller constituent portions 81 a and 82 a in the vertical direction, and an eccentric portion 60 a provided in the middle of the shaft 60 and whose center axis is deviated from the center axis of the shaft 60 is a roller configuration. It is fitted in the space inside the portions 81a and 82a. Thereby, in the piston 62, when the shaft 60 rotates, the roller constituting portions 81a and 82a are arranged so that the outer peripheral surfaces 81c and 82c are on the cylinder chamber 71 side as shown in FIGS. 2 (a) to 2 (d). It moves to the clockwise direction of FIG. 2 along the side wall surface 71a so that it may contact | abut to the wall surface 71a.

  As the piston 62 moves in this manner, the cylinder chamber 71 is divided into the low pressure chamber 71c and the high pressure chamber 71d by the piston 62, and the volumes of the low pressure chamber 71c and the high pressure chamber 71d change, and FIG. As shown in FIG. 4, the outer peripheral surfaces 81c and 82c of the roller constituent portions 81a and 82a abut against the portion adjacent to the downstream side of the inlet port 71b on the side wall surface 71a of the cylinder chamber 71 in the moving direction of the roller constituent portions 81a and 82a. After reaching the state, until the state shown in FIG. 2D is reached, the volume of the high pressure chamber 71d is reduced and the refrigerant in the high pressure chamber 71d is compressed. When the state shown in FIG. 2D is reached, the refrigerant compressed to a predetermined pressure or higher in the high pressure chamber 71 d is discharged from the discharge port 74 to the sealed space 26. During this time, the refrigerant to be compressed next is introduced into the low pressure chamber 71c from the introduction port 71b. By repeating the operation as described above, the compressed refrigerant accumulates in the sealed space 26, and the refrigerant accumulated in the sealed space 26 is discharged to the outside from the discharge passage 25.

  At this time, the piston 62 contacts the upper and lower wall surfaces of the cylinder chamber 71 (the wall surfaces on both sides of the cylinder chamber 71 in the axial direction of the cylinder 61), that is, the front head 63, the middle plate 64, and the rear head 65. 4 and 5, as shown in FIGS. 4 and 5, the total height Hp (= [Hp / 2] + [Hp] of the height of the piston 62, that is, the height of the two piston constituent members 81 and 82, is used. / 2]) is lower than the height Hs of the cylinder chamber 71.

  However, if the piston constituent members 81 and 82 are too low, an oil film of the lubricating oil L is not formed between the inner peripheral surfaces 81d and 82d of the roller constituent portions 81a and 82a and the side surfaces of the eccentric portion 60a. There is a concern that the component members 81 and 82 and the eccentric portion 60a are in direct contact with each other and seizure occurs. However, in this reference example, the height Hp / 2 of the piston constituent members 81 and 82 is set so that the inner peripheral surfaces 81d and 82d of the roller constituent portions 81a and 82a and the shaft 60 (eccentricity) as shown in FIG. The height of the oil film of the lubricating oil L is formed between the side surface of the portion 60a) and the roller constituting portions 81a and 82a and the eccentric portion 60a are not in direct contact with each other. It is prevented that the two come into contact with each other and burn-in occurs.

  Thus, since the height Hp of the piston 62 is lower than the height Hs of the cylinder chamber 71, the gap between the upper surface of the roller component 81a and the upper wall surface of the cylinder chamber 71, and the roller component Lubricating oil L flows into the low-pressure chamber 71c from the inside of the roller constituting portions 81a and 82a through a gap between the lower surface of 82a and the lower wall surface of the cylinder chamber 71. When the amount of the lubricating oil L flowing into the low pressure chamber 71c from the inside of the roller constituting portions 81a and 82a increases, the temperature of the refrigerant in the low pressure chamber 71c increases due to the lubricating oil L, and the performance of the compressor 1 decreases. There is a risk that.

  Furthermore, the gap between the upper surface of the blade component 81b and the upper wall surface of the cylinder chamber 71 and the gap between the lower surface of the blade component 82b and the lower wall surface of the cylinder chamber 71 are set in the high pressure chamber 71d. Lubricating oil L flows. Since the refrigerant is compressed in the high pressure chamber 71d as described above, the temperature of the refrigerant in the high pressure chamber 71d is high, and the amount of the lubricating oil L flowing from the high pressure chamber 71d into the low pressure chamber 71c increases. The lubricating oil L may increase the temperature of the refrigerant in the low pressure chamber 71c and reduce the performance of the compressor 1.

  However, in this reference example, since the piston 62 is configured by stacking the two piston constituent members 81 and 82 in the vertical direction, the piston 62 is disposed between the upper surface of the piston constituent member 81 and the upper wall surface of the cylinder chamber 71. In addition to the gap between the lower surface of the piston component member 82 and the lower wall surface of the cylinder chamber 71, the lubricating oil L also flows between the piston component member 81 and the piston component member 82 to form an oil film. Can do.

  Therefore, as shown in FIGS. 4 (b) and 5 (b), when the piston 62 ′ is constituted by one member as in the prior art, the height of the piston 62 ′ is Assuming that Hp is the same as the total height of the piston constituting members 81 and 82, the size B1 of the gap between the upper surface of the piston 62 'and the upper wall surface of the cylinder chamber 71 in this case, and the lower surface of the piston 62' The sum B1 + B2 of the size B2 of the gap between the cylinder wall 71 and the wall surface of the cylinder chamber 71 is the size of the gap A1 between the upper surface of the piston component 81 and the upper wall surface of the cylinder chamber 71 in this reference example. , The same as the total A1 + A2 + A3 of the size A2 of the gap between the lower surface of the piston component 82 and the lower wall surface of the cylinder chamber 71 and the size A3 of the gap between the piston component 81 and the piston component 82 That.

  Further, the sizes A1, A2, and A3 of the gaps in the case of this reference example are substantially equal (that is, the size of about one third of the total of these gaps). On the other hand, the sizes B1 and B2 of the gaps in the conventional case are also substantially equal (that is, about a half of the total of these gaps). Accordingly, in the case of this reference example, the sizes A1, A2, and A3 of the gaps in this reference example are as shown in FIG. 4 (to the extent that there is a gap between the piston component member 81 and the piston component member 82. b) The gaps B1 and B2 are smaller than the gaps shown in FIG.

であることが知られている。ここで、ｈは隙間の大きさ、μは潤滑油Ｌの粘度、ｄｐ／ｄｘは圧力勾配である。そして、この式から、平板間の隙間を流れる液体の流量Ｑは、隙間の大きさｈの３乗に比例するため、隙間が複数あり、隙間の大きさの合計が同じ場合には、隙間の数が多く各隙間の大きさが小さいほうが、液体の流量Ｑの合計が少なくなることが分かる。 Here, from the viewpoint of hydrodynamics, the flow rate Q of the liquid flowing through the gap between the two flat plates is

It is known that Here, h is the size of the gap, μ is the viscosity of the lubricating oil L, and dp / dx is the pressure gradient. From this equation, the flow rate Q of the liquid flowing through the gap between the flat plates is proportional to the cube of the gap size h. It can be seen that the larger the number and the smaller the size of each gap, the smaller the total liquid flow rate Q.

  Therefore, when the piston 62 is constituted by two piston constituent members 81 and 82 stacked in the vertical direction as in this reference example, the upper surface of the piston constituent member 81 and the upper wall surface of the cylinder chamber 71 The sizes A1, A2, and A3 of the gap between the lower surface of the piston component member 82 and the lower wall surface of the cylinder chamber 71 and the gap between the piston component member 81 and the piston component member 82 may be reduced. It is possible to reduce the amount of the lubricating oil L flowing into the low-pressure chamber 71c from the high-pressure chamber 71d and the roller constituent portions 81a and 82a through these gaps. Thereby, it can prevent that the temperature of the refrigerant | coolant in the low pressure chamber 71c rises with the high temperature lubricating oil L, and can prevent that the performance of the compressor 1 falls.

  Alternatively, in the case where the amount of the lubricating oil L flowing into the low pressure chamber 71c may be the same as the conventional one, the total size of the gaps A1 + A2 + A3 should be larger than the conventional total size of the gaps B1 + B2. That is, since the sum of the height of the piston component 81 and the height of the piston component 82 can be made lower than the height of the piston 62 ′, the piston 62 comes into contact with the upper and lower wall surfaces of the cylinder chamber 71 and the piston It is possible to reliably prevent the movement of 62 from being hindered.

  Here, in the case of this reference example, since the gap sizes A1 and A2 are smaller than the conventional gap sizes B1 and B2, the upper surface of the piston component 81 and the cylinder chamber 71 The upper wall surface, the lower surface of the piston component member 82, and the lower wall surface of the cylinder chamber 71 are arranged closer to each other, and the piston component members 81 and 82 are in contact with the upper and lower wall surfaces of the cylinder chamber 71. It is thought that it is easy to end.

  However, when the piston constituent members 81 and 82 and the upper and lower wall surfaces of the cylinder chamber 71 approach each other due to a difference in the amount of linear expansion deformation between the cylinder 61 and the piston 62, the piston constituent members 81 and 82 and the upper and lower wall surfaces of the cylinder chamber 71 And the oil film formed by the lubricating oil L between the piston component member 81 and the piston component member 82 is crushed so that the piston component member 81 and the piston component member 82 move toward each other (that is, If the piston component 81 and the piston component 82 move until there is no gap between them, the space between the upper surface of the piston component 81 and the upper wall surface of the cylinder chamber 71 is reduced. And, between the lower surface of the piston component member 82 and the lower wall surface of the cylinder chamber 71, the field of the conventional piston 62 ' Since the same by a gap so that it is between, as compared to conventional, piston 62 is not that easy to cause contact with the upper and lower wall of the cylinder chamber 71.

  Further, here, even if the piston component member 81 and the piston component member 82 are stacked in the vertical direction, unlike the above description, there is no gap between the piston component member 81 and the piston component member 82. 4A and 5A, the distances A1 and A2 between the piston constituent members 81 and 82 and the upper and lower wall surfaces of the cylinder chamber 71 are respectively shown in FIG. 4B. The distances B1 and B2 shown in FIG. 5B are almost the same, that is, the distances A1 and A2 may not be smaller than the distances B1 and B2.

  However, in this reference example, as shown in FIG. 6A, the shaft 60 rotates and the piston components 81 and 82 move with no gap between the piston component 81 and the piston component 82. Then, a pressing force acts between the outer peripheral surface of the eccentric portion 60a and the inner peripheral surfaces 81d and 82d of the roller constituting portions 81a and 82a, and the lubricating oil L positioned therebetween is crushed by this force. The force (oil film reaction force) that pushes back from the lubricating oil L acts on the inner peripheral surfaces 81d and 82d. Here, FIG. 6A shows an oil film reaction force generated between the piston 62 and the eccentric portion 60a of the shaft 60 in the state where there is no gap between the two piston components 81 and 82, and the magnitude thereof. FIG.

  As shown in FIG. 6 (a), the magnitude of this oil film reaction force is the central portion of the piston constituent members 81, 82 in the vertical direction, that is, between the piston constituent member 81 and the piston constituent member 82. Because the oil film reaction force causes the lubricating oil L to flow between the piston component member 81 and the piston component member 82, a gap is formed between them. Therefore, during the operation of the compressor 1, a gap is surely formed between the piston component member 81 and the piston component member 82.

  In addition, the magnitude | size of the said oil film reaction force after the clearance gap was made between the piston structural member 81 and the piston structural member 82 is the up-down direction of the piston structural members 81 and 82, as shown in FIG.6 (b). The larger the central part, the smaller the upper and lower end parts. Here, FIG. 6B shows an oil film reaction force generated between the piston 62 and the eccentric portion 60a of the shaft 60 in a state where a gap is formed between the two piston constituent members 81 and 82, and its magnitude. It is a figure which shows distribution of thickness.

  Further, as shown in FIGS. 4B and 5B, when the piston 62 ′ is constituted by one member, the blade portion of the piston 62 ′ (the blade component shown in FIG. 5B). There is a risk that heat will be trapped in the substantially central part in the vertical direction of the portions (corresponding to 81b and 82b) and seizure will occur.

  However, in this reference example, the piston 62 is constituted by two piston constituent members 81 and 82 stacked in the vertical direction, and the lubricating oil L flows between the blade constituent portion 81b and the blade constituent portion 82b. Heat is not trapped between the blade constituent part 81b and the blade constituent part 82b, and it is possible to prevent the image sticking as described above from occurring.

Further, in the compressor 1 can be used CO ₂ as a refrigerant. When CO ₂ is used as the refrigerant, the pressure difference between the low pressure chamber and the high pressure chamber becomes particularly large, and the lubricating oil L tends to flow from the high pressure chamber 71d to the low pressure chamber 71c. However, even in such a case, as described above, between the upper surface of the piston component member 81 and the upper wall surface of the cylinder chamber 71, between the lower surface of the piston component member 82 and the lower wall surface of the cylinder chamber 71, and the piston Through the gap between the component member 81 and the piston component member 82, the amount of the lubricating oil L flowing into the roller component portions 81a and 82a and from the high pressure chamber 71d to the low pressure chamber 71c can be reduced.

Further, in the compressor 1 using CO ₂ as the refrigerant, the temperature of the refrigerant discharged from the compressor 1 becomes high when used in a hot water supply device, and therefore the temperature is lowered from the high pressure chamber 71d having a high temperature. When the lubricating oil L flows into the low pressure chamber 71c, the temperature of the refrigerant in the low pressure chamber rises, and the compression efficiency of the refrigerant in the compressor 1 may decrease.

  However, in this reference example, as described above, between the upper surface of the piston component member 81 and the upper wall surface of the cylinder chamber 71, between the lower surface of the piston component member 82 and the lower wall surface of the cylinder chamber 71, and the piston configuration Since the amount of the lubricating oil L flowing into the low pressure chamber 71c from the high pressure chamber 71d and the inside of the roller configuration portions 81a and 82a through the gap between the member 81 and the piston constituent member 82 can be reduced, Such a decrease in the compression efficiency of the refrigerant can be reduced.

In the compressor 1, the refrigerant is represented by a molecular formula of C ₃ H _m F _n (where m = 1 to 5, n = 1 to 5, and m + n = 6), and in the molecular structure. It is also possible to use a single refrigerant composed of a refrigerant having one double bond or a mixed refrigerant containing the refrigerant.

Specifically, 2,3,3,3-tetrafluoro-1-propene (referred to as “HFO-1234yf”, the chemical formula is represented by CF 3 -CF═CH 2), 1, 2, 3, 3-penta Fluoro-1-propene (referred to as “HFO-1225ye”, the chemical formula is represented by CF ₃ —CF═CHF), 1, _{3, 3,} 3-tetrafluoro-1-propene (referred to as “HFO-1234ze”) The chemical formula is represented by CHF ₂ —CF═CHF), 1, _2, 3, 3-tetrafluoro-1-propene (“HFO-1234ye”), and the chemical formula is represented by CHF ₂ —CF═CHF. ) 3,3,3-trifluoro-1-propene (referred to as “HFO-1234zf”, the chemical formula is represented by CF ₃ —CH═CH ₂ ), 1,2,2-trifluoro-1-propene (Chemical formula is C ₃ represented by -CF = CF _2), 2- fluoro-1-propene (a chemical formula thereof is represented by _CH 3 -CF = _{CH 2)} which may be used.

  Furthermore, HFC-32 (difluoroethane), HFC-125 (pentafluoroethane), HFC-134 (1, 1, 2, 2-tetrafluoroethane), HFC-134a (1, 1, 1) are added to the refrigerant described above. 2-tetrafluoroethane), HFC-143a (1,1,1-trifluoroethane), HFC-152a (1,1-difluoroethane), HFC-161, HFC-227ea, HFC-236ea, HFC-236fa, A mixed refrigerant in which at least one of HFC-365mfc, methane, ethane, propane, propene, butane, isobutane, pentane, 2-methylbutane, cyclopentane, dimethyl ether, bis-trifluoromethyl-sulfide, carbon dioxide, and helium is added. It is also possible to use it.

The refrigerant (C ₃ H _m F _n) as described above has a relatively high coefficient of performance (COP) in theory, and the coefficient of performance (COP) of the apparatus using the compressor 1 is improved. Further, it is known that such a refrigerant does not contain chlorine atoms, bromine atoms, or the like and has a small influence on the destruction of the ozone layer (low global warming potential (GWP)).

  However, since the refrigerant as described above has a relatively low refrigeration capacity per unit volume, it is necessary to increase the volume of the cylinder chamber 71 as compared with the case where other refrigerants are used. At this time, it is conceivable to increase the height of the cylinder chamber 71 in order to increase the volume of the cylinder chamber 71. However, when the height of the cylinder chamber 71 is increased, the cylinder chamber 71 is disposed in the cylinder chamber 71. The piston height also increases. Therefore, when the piston is constituted by a single member as in the prior art (for example, like the piston 62 ′ shown in FIG. 4B and FIG. 5B), it is particularly at the center of the blade portion of the piston. Heat tends to be trapped, and baking tends to occur.

  On the other hand, in this reference example, since the piston 62 is configured by stacking the piston component member 81 and the piston component member 82, heat is generated between the blade component portion 81b and the blade component portion 82b. It is possible to reliably prevent the occurrence of burn-in as described above without being stuffed.

  In addition, since the refrigerant as described above is easily decomposed at a high temperature, it is desirable to be used in a situation where it is difficult to attain a high temperature. However, in this reference example, as described above, the piston 62 is likely to have a high temperature. Since the portion between the piston component 81 and the piston component 82 of the piston 62 corresponding to the substantially central portion in the vertical direction of 'is cooled by the lubricating oil L, the refrigerant is prevented from being decomposed. be able to.

  As described above, in the compressor 1 of the present reference example, the piston 62 is constituted by the two piston constituent members 81 and 82 stacked in the vertical direction, and therefore, the upper surface of the piston constituent member 81 and the cylinder chamber 71 The size A1 of the gap between the upper wall surface, the size A2 of the gap between the lower surface of the piston component member 82 and the lower wall surface of the cylinder chamber 71, and the gap between the piston component member 81 and the piston component member 82 Even if the total A1 + A2 + A3 of the sizes A3 is the same as the sum of the sizes B1 + B2 between the piston 62 'formed by one member and the upper and lower wall surfaces of the cylinder chamber as in the prior art, the size of each gap Since the sizes of A1, A2, and A3 are smaller than the sizes of the gaps B1 and B2 in the conventional case, the size is lower than the inner side of the roller constituting portions 81a and 82a and the high pressure chamber 71d. It is possible to reduce the amount of lubricant L which flows into the chamber 71c. Thereby, it becomes difficult for the temperature of the refrigerant | coolant in the low pressure chamber 71c to rise with the lubricating oil L, and it can prevent that the performance of the compressor 1 falls.

  Or when making the quantity of the said lubricating oil L which flows into the low pressure chamber 71c into the same level as the past, the sum total of the height of the piston structural members 81 and 82 can be made small, and piston structural members 81 and 82 are cylinders. Contact with the upper and lower wall surfaces of the chamber 71 can be reliably prevented.

  In addition, since the lubricating oil L flows between the blade component 81b and the blade component 82b, heat is trapped between the blade component 81b and the blade component 82b to prevent seizure. be able to.

  Further, since the piston constituent members 81 and 82 are formed integrally with the roller constituent portion 81a and the blade constituent portion 81b, and the roller constituent portion 82a and the blade constituent portion 82b, respectively, It is possible to prevent seizure from occurring due to sliding of the 81a and the blade constituting portion 81b and the roller constituting portion 82a and the blade constituting portion 82b.

  In the reference example 1 described above, the piston 62 is configured by the two piston constituent members 81 and 82 stacked in the vertical direction, but is not limited thereto. In Reference Example 2, as shown in FIG. 7, the piston 90 is configured by three piston constituent members 91, 92, and 93 having a height of about Hp / 3, which are stacked in the vertical direction (Reference Example 2). .

  Even in this case, the lubricating oil L (see FIG. 4) flows between the piston component 91 and the piston component 92 and between the piston component 92 and the piston component 93 to form an oil film. Since there is a gap, a gap between the upper surface of the piston component member 91 and the upper wall surface of the cylinder chamber 71 (see FIG. 4), a gap between the lower surface of the piston component member 93 and the lower wall surface of the cylinder chamber 71, and The size of the gap between the piston constituent members 91 to 93 is smaller than the conventional one (specifically, B1 and B2 described above). Thus, as in the above-described embodiment, lubrication flows into the low-pressure chamber 71c (see FIG. 4) from the high-pressure chamber 71d (see FIG. 4) and the roller constituent portions 91a, 92a, and 93a through these gaps. The amount of oil L can be reduced.

  Further, since the lubricating oil L flows between the blade constituent portions 91b, 92b, and 93b, it is possible to prevent heat from being burned and burnt in the portion between the blade constituent portions 91b, 92b, and 93b. .

  However, also in Reference Example 2, the height Hp / 3 of each piston component 91 to 93 is between the inner peripheral surfaces 91d, 92d, 93d of the roller components 91a, 92a, 93a and the eccentric portion 60a. The height is such that an oil film of the lubricating oil L can be formed.

  Further, four or more piston constituent members may be stacked in the vertical direction. However, as the number of piston components increases, the height of each piston component decreases, so the number of piston components depends on the inner peripheral surface of the roller component. It is necessary to make the number more than the minimum height at which an oil film is formed between the first and second eccentric portions 60a.

  Further, in the above-described reference example 1, in the piston constituent members 81 and 82, the roller constituent portion 81a and the blade constituent portion 81b, and the roller constituent portion 82a and the blade constituent portion 82b are integrally formed, respectively. The roller and the blade were integrally formed. In the embodiment of the present invention, as shown in FIGS. 8 and 9, a substantially annular roller 101 in a plan view is disposed in the cylinder chamber 71, and the blade 102 includes the cylinder chamber 71 and the blade storage chamber. 105. Further, a spring 103 that presses the blade 102 toward the roller 101 downward in FIG. 8 is disposed at the upper end of the blade storage chamber 105 in FIG. The roller 101 includes two roller constituent members 111 and 112 stacked in the vertical direction, and the blade 102 includes two blade constituent members 113 and 114 stacked in the vertical direction.

  As described above, even when the roller 101 and the blade 102 are formed separately, the upper surface of the roller component member 111 and the upper surface of the blade component member 113 and the upper surface of the cylinder chamber 71 are the same as in the above-described embodiment. A gap between the wall surface, a lower surface of the roller component member 112, a gap between the lower surface of the roller component member 112 and the lower wall surface of the cylinder chamber 71, a gap between the roller component member 111 and the roller component member 112, and The gap between the blade constituent member 113 and the blade constituent member 114 is reduced, and the amount of lubricating oil L flowing into the low pressure chamber 71c from the inside of the roller constituent members 111 and 112 and the high pressure chamber 71d is reduced.

  Further, since the lubricating oil L also flows between the blade constituent member 113 and the blade constituent member 114, heat is burnt into the portion between the blade constituent member 113 and the blade constituent member 114 as in the above-described embodiment. The occurrence of sticking is prevented.

In addition, when a refrigerant containing C ₃ H _m F _n as described in the above embodiment is used as the refrigerant, the refrigerant is easily decomposed at a high temperature, so that it is used in a situation where it is difficult to achieve a high temperature. It is desirable. On the other hand, in the compressor in which the roller and the blade are separated as in the second modification, heat is generated by sliding between the roller and the blade, and this portion of the compressor is likely to become high temperature.

  However, in this embodiment, as described above, the roller 101 is configured by the two roller constituent members 111 and 112 that are stacked in the vertical direction, and the blade 102 is the two blades that are stacked in the vertical direction. Since it is constituted by the constituent members 113 and 114, the lubricating oil L flows between the roller constituent member 111 and the roller constituent member 112 and between the blade constituent member 113 and the blade constituent member 114. This part of the compressor is cooled. Therefore, it is possible to prevent the refrigerant from being decomposed due to the temperature rise of the compressor.

  In the present embodiment, the roller 101 is configured by the two roller constituent members 111 and 112 and the blade 102 is configured by the two blade constituent members 113 and 114. However, the present invention is not limited thereto. .

  In another reference example 3, as shown in FIG. 10, the roller 101 is configured by two roller constituent members 111 and 112 as in the reference example 1, but the blade 102 is configured by one member. (Reference Example 3). Even in this case, the amount of the lubricating oil L flowing into the low-pressure chamber 71c from the inside of the roller constituent members 111 and 112 can be reduced as in the above-described embodiment.

Furthermore, in Reference Example 4 , as shown in FIG. 11, the blade 102 is configured by two blade constituent members 113 and 114 as in the present embodiment, but the roller 101 is configured by one member. ( Reference Example 4 ). Even in this case, the amount of the lubricating oil L flowing from the high pressure chamber 71d into the low pressure chamber 71c can be reduced, and the portion between the blade component member 113 and the blade component member 114 can be heated as in the above-described embodiment. It is possible to prevent the occurrence of burning burning.

  Further, when the roller 101 is composed of a plurality of roller constituent members and the blade 102 is composed of a plurality of blade constituent members, the number of roller constituent members and the number of blade constituent members are different from each other. Also good. Even in this case, the same effects as those of the present embodiment described above can be obtained.

  In the reference example and the embodiment described above, the shaft 60 extends in the vertical direction (the axial direction of the cylinder 61 is the vertical direction), and the piston constituent members 81 and 82 are stacked in the vertical direction. However, the present invention is not limited to this, and when the shaft extends in the horizontal direction (when the axial direction of the cylinder is the horizontal direction), a plurality of piston constituent members are stacked in the extending direction of the shaft (axial direction of the cylinder). It may be.

  As mentioned above, although embodiment of this invention was described based on drawing, specific structure is not restricted to these embodiment, It can change in the range which does not deviate from the summary of invention. In addition, the above embodiment is an essentially preferable illustration, Comprising: It does not intend restrict | limiting the range of this invention, its application thing, or its use.

  If the present invention is used, the amount of lubricating oil flowing into the low pressure chamber can be reduced, and the lubricant can prevent the temperature of the refrigerant in the low pressure chamber from rising and the performance of the compressor from being deteriorated. it can.

DESCRIPTION OF SYMBOLS 1 Compressor 12 Motor 13 Compression mechanism 24 Inlet 26 Sealed space 61 Cylinder 62 Piston 71 Cylinder chamber 71a Side wall surface 71c Low pressure chamber 71d High pressure chamber 81, 82 Piston component 81a, 82a Roller component 81b, 82b Blade component 81c, 82c Outer peripheral surface 91, 92, 93 Piston component 101 Roller 102 Blade 111, 112 Roller component 113, 114 Blade component

Claims (1)

A cylinder disposed in a sealed space and having a cylinder chamber therein;
The cylinder chamber is arranged inside the cylinder chamber and moves along the side wall surface so that the outer peripheral surface thereof abuts on the side wall surface of the cylinder chamber, and the cylinder chamber is compressed while the refrigerant is compressed. An annular roller that changes the volume of the high pressure chamber and the low pressure chamber, and a high pressure chamber that discharges the refrigerant into the sealed space and a low pressure chamber into which the refrigerant is introduced from the outside,
A blade that is disposed inside the cylinder chamber and divides the cylinder chamber into the high-pressure chamber and the low-pressure chamber together with the roller;
A spring that presses the blade toward the roller;
The roller is constituted by a plurality of roller constituent members stacked in the axial direction of the cylinder,
The compressor is configured by a plurality of blade constituent members that are stacked in the axial direction of the cylinder and pressed toward the roller by the one spring.

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