JP2008180178A - Rotary compressor and refrigeration cycle equipment - Google Patents

Abstract

An object of the present invention is to increase the amount of eccentricity of an eccentric part of a rotating shaft, to reduce the diameter of the eccentric part without reducing the diameter of the main shaft part and the auxiliary shaft part, and to ensure the strength reliability of the rotating shaft. In addition, there are provided a rotary compressor capable of smoothly assembling an eccentric part of a roller and improving workability, and a refrigeration cycle apparatus provided with the rotary compressor and capable of improving refrigeration efficiency.
A main shaft portion 4a pivotally supported by a main bearing 9, a subshaft portion 4b pivotally supported by a sub bearing 10, and an eccentric roller 15 provided between the main shaft portion and the sub shaft portion and engaged with each other. In a rotary compressor including a rotating shaft 4 having an eccentric portion 4c and a cylinder 7 having a cylinder chamber 8 in which an eccentric roller moves eccentrically while contacting the peripheral surface, the shaft diameter of the main shaft portion is φD1, When the shaft diameter of the shaft portion is φD2, the shaft diameter of the eccentric portion is φD3, and the amount of eccentricity of the eccentric portion is E, both of φD3 <φD1 + 2 × E (1) and φD3 <φD2 + 2 × E (2) And an escape portion L for assembling the eccentric roller to the eccentric portion.
[Selection] Figure 1

Description

  The present invention relates to a rotary compressor having an improved compression mechanism, and a refrigeration cycle apparatus including the rotary compressor and constituting a refrigeration cycle.

In a refrigeration cycle apparatus that constitutes a refrigeration cycle by connecting a compressor, a condenser, an expansion device, and an evaporator via a refrigerant pipe, a so-called rotary compressor (“rotary compressor”) is used as the compressor. Is often used).
In this type of rotary compressor, in order to reduce friction loss and improve compression efficiency, it is desirable to reduce the diameter of the eccentric portion (crank portion) having the largest diameter at the sliding portion of the rotating shaft as much as possible. . At the same time, it is preferable to reduce the sliding loss of the rotating shaft by further reducing the thickness of the cylinder and increasing the amount of eccentricity of the eccentric portion.

The rotating shaft includes a main shaft portion pivotally supported by the main bearing, a subshaft portion pivotally supported by the sub-bearing, and an eccentric portion provided between the main shaft portion and the sub-shaft portion and fitted with an eccentric roller. It has. Normally, the shaft diameter φD1 of the main shaft portion and the shaft diameter φD2 of the sub shaft portion are set to be equal to each other, the shaft diameter of the eccentric portion is φD3, and the amount of eccentricity of the eccentric main shaft portion and the sub shaft portion with respect to the shaft center is E When
φD3 <φD1 (= φD2) + E
By setting as above, the diameters of the eccentric part and the cylinder chamber are reduced, and the above-mentioned advantageous conditions are obtained.

  However, when the roller is inserted from the end surface of the main shaft portion in order to fit the eccentric roller to the eccentric portion with the above setting, the end portion on the non-insertion side of the roller is in a state where the insertion side end surface of the roller is in contact with the eccentric portion end surface. Still not coming out of the main shaft. Even if the roller is moved to any position in the radial direction, it cannot be fitted into the eccentric portion. Further, when the roller is inserted from the end surface of the countershaft portion, the subshaft portion shaft diameter φD2 and the main shaft portion shaft diameter φD1 are the same, so the roller cannot be assembled to the eccentric portion.

Therefore, in [Patent Document 1], the diameter of the sub-shaft portion is made smaller than the diameter of the main shaft portion, and the outer peripheral surface of the eccentric portion on the side opposite to the eccentric direction is recessed from the outer peripheral surface of the main shaft portion. A technique is disclosed in which a connecting portion connecting the portions is provided with a portion having a diameter smaller than the outer diameter of the main shaft portion, and the axial length of the small diameter portion is equal to or greater than the height of the roller fitted to the main shaft portion. .
JP 2003-328972 A

  If it comprises like said [patent document 1], a roller will be inserted from a countershaft part end surface, the eccentric part by the side of a countershaft part will be passed, and once between a subshaft part and a main shaft part (connection part) Can be located. Then, the roller can be assembled to the eccentric portion on the main shaft portion side, and thereafter, if another roller is assembled to the eccentric portion on the auxiliary shaft portion side, the assembling operation is easily completed.

  As described above, in the technique of [Patent Document 1], the roller is rotated while the shaft diameter of the eccentric portion is smaller (φD3 <φD1 + 2 × E) than the length obtained by adding twice the amount of eccentricity to the shaft diameter of the main shaft portion. It can be easily assembled to the shaft eccentric part.

  However, [Patent Document 1] presupposes that the diameter of the sub-shaft portion is reduced (φD3> φD2 + 2 × E). For this reason, in order to reduce the sliding loss of the rotary shaft, the shaft diameter of the eccentric portion is made as small as possible and the eccentric amount of the eccentric portion is set to be large. It becomes too thin, and in particular results in a problem in reliability of the strength of the countershaft.

  The present invention has been made on the basis of the above circumstances, and the object of the present invention is to increase the eccentric amount of the eccentric portion of the rotating shaft and reduce the eccentric portion shaft diameter without reducing the shaft diameter of the main shaft portion and the sub shaft portion. A rotary compressor that can reduce the size of the rotating shaft, ensure the reliability of the strength of the rotating shaft, and can smoothly assemble the eccentric part of the roller to improve workability, and improve the refrigeration efficiency with this rotary compressor. It is an object of the present invention to provide a refrigeration cycle apparatus that can achieve the conversion.

In order to satisfy the above object, the rotary compressor of the present invention is provided eccentrically between the main shaft portion pivotally supported by the main bearing, the subshaft portion pivotally supported by the sub-bearing, and the main shaft portion and the sub-shaft portion. A rotating shaft having an eccentric portion with which the roller engages, and a cylinder having a cylinder chamber that accommodates the roller and moves eccentrically while contacting the peripheral surface as the rotating shaft rotates. When the shaft diameter is φD1, the shaft diameter of the auxiliary shaft portion is φD2, the shaft diameter of the eccentric portion is φD3, and the eccentric amount of the eccentric portion is E,
φD3 <φD1 + 2 × E (1)
φD3 <φD2 + 2 × E (2)
(1) and (2) are satisfied and at least one of the main shaft portion and the sub-shaft portion or the roller of the rotating shaft is eccentrically arranged via the main shaft portion or the sub-shaft portion. Equipped with escape means when assembled to the part.

  In order to satisfy the above object, the refrigeration cycle apparatus of the present invention comprises a condenser, an expansion device, and an evaporator together with the rotary compressor described above to constitute a refrigeration cycle.

According to the rotary compressor of the present invention, the eccentric portion is made as small as possible to reduce the load and frictional force applied to the rotating shaft, the distance between the eccentric portions of the rotating shaft is shortened, and the compression performance is improved and improved. There are effects such as reliability.
Furthermore, according to the refrigeration cycle apparatus of the present invention, the rotary compressor is provided, and the effects of improving the refrigeration cycle efficiency and obtaining high reliability are achieved.

Hereinafter, a first embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a schematic configuration diagram of a sectional structure of a rotary compressor A and a refrigeration cycle apparatus including the rotary compressor A. (In order to avoid complications in the drawings, some components that are not denoted by reference numerals are not shown in the drawings. (The same applies hereinafter)
First, the configuration of the refrigeration cycle apparatus will be described. The rotary compressor A, the condenser B, the expansion device C such as an electronic expansion valve, the evaporator D, and a gas-liquid separator (not shown) are provided. The components are sequentially communicated via the refrigerant pipe P. As will be described later, the refrigerant gas compressed by the rotary compressor A is guided to the refrigerant pipe P and circulates in the order of the above components to form a refrigeration cycle, and is sucked into the rotary compressor A again. It has become.

In the rotary compressor A, reference numeral 1 in the drawing denotes a bottomed cylindrical case main body 1a having an open upper end, and a cup-shaped lid case 1b that closes the upper end opening of the case main body 1a using welding means or the like. It is a sealed case consisting of
The refrigerant pipe P is vertically connected to the axial center position of the lid case 1b, and this open end projects through the lid case 1b and protrudes into the sealed case 1. The refrigerant gas compressed by the rotary compressor A is led from the protruding refrigerant pipe P to the condenser B. On the other hand, the refrigerant pipe P is connected in a horizontal state to the lower part of the case body 1a. The refrigerant gas is sucked into the rotary compressor A through the horizontal refrigerant pipe P from the gas-liquid separator.

  A compression mechanism portion 2 is accommodated in the lower portion of the sealed case 1, and an electric motor portion 3 is accommodated in the upper portion of the compression mechanism portion 2. The compression mechanism section 2 and the electric motor section 3 are connected via a rotating shaft 4, and the compression mechanism section 2 is driven by the electric motor section 3 via the rotating shaft 4 as will be described later.

  For example, a brushless DC synchronous motor (which may be an AC motor or a commercial motor) is used as the electric motor unit 3. The electric motor unit 3 includes a stator 5 that is fixed to the inner peripheral surface of the sealed case 1 through a process such as shrink fitting, and a rotor 6 that is disposed with a predetermined gap on the axial center side of the stator 5. The The rotating shaft 4 is fitted and fixed along the axis of the rotor 6.

  A plurality of concave grooves are provided along the axial direction on the outer circumferential surface of the stator 5 with a predetermined gap in the circumferential direction, and a narrow gap is formed between the inner circumferential surface of the case body 1a. The concave groove and the gap are flow passages through which the refrigerant gas compressed by the compression mechanism unit 2 flows.

Next, the compression mechanism unit 2 will be described.
In the figure, reference numeral 7 denotes a cylinder that is fitted into the inner peripheral surface of the case main body 1a in a press-fitted state and is attached and fixed from the outer peripheral surface of the case main body 1a by means such as spot welding. This cylinder 7 is provided with a hole 8 extending along the axis, and has a substantially ring shape.

  A main bearing 9 is attached and fixed via a mounting bolt a at a position where the hole 8 is closed on the upper surface of the cylinder 7. Further, the auxiliary bearing 10 is attached and fixed via the attachment bolt b at a position where the hole 8 is blocked by the lower surface of the cylinder 7. The hole 8 of the cylinder 7 is a space chamber surrounded by the main bearing 9 and the auxiliary bearing 10, and the cylinder chamber 8 is formed.

  The refrigerant pipe P extending from the gas-liquid separator to the rotary compressor A passes through the wall of the sealed case 1 and is connected to the circumferential surface of the cylinder 7. A suction passage is provided between a portion of the cylinder 7 to which the refrigerant pipe P is connected and the cylinder chamber 8. Therefore, the refrigerant pipe P penetrates the sealed case 1 and communicates with the cylinder chamber 8 through the suction passage of the cylinder 7.

  The main bearing 9 protrudes toward the electric motor unit 3 along the shaft core, and is integrally formed at a lower end of the bearing unit 9a with a bearing unit 9a that pivotally supports a part of the rotating shaft 4, and is attached by the mounting bolt a. It consists of a flange 9b that is directly attached and fixed to the upper surface of the cylinder 7. The rotating shaft 4 portion pivotally supported by the bearing portion 9a is referred to as a “main shaft portion 4a”.

A discharge valve mechanism is provided at a portion facing the cylinder chamber 8 of the main bearing collar 9b. This discharge valve mechanism opens on the upper surface of the flange 9b and is covered with a valve cover 12 provided over the upper surface of the flange 9b and the upper end of the bearing 9a.
The auxiliary bearing 10 projects toward the bottom of the sealed case 1 along the shaft core, and is integrally formed at the lower end of the bearing 10a and the bearing 10a that pivotally supports the lower end of the rotary shaft 4, and the mounting bolt It consists of a flange 10b that is attached and fixed to the lower surface of the cylinder 7 by b. The rotating shaft 4 portion pivotally supported by the bearing portion 10a is referred to as a “sub shaft portion 4b”.

For the reason described later, the thickness of the flange portion 10b of the auxiliary bearing 10 is formed larger than the thickness of the flange portion 9b of the main bearing 9. On the other hand, a discharge valve mechanism is provided on the flange portion 10 b of the auxiliary bearing 10, and the lower end opening is covered with a valve cover 13.
In the rotating shaft 4, an auxiliary escape portion f, an eccentric portion 4c, and a connecting portion 4d are connected in order from the upper portion to the lower portion between the main shaft portion 4a and the sub shaft portion 4b. Although these auxiliary escape parts f etc. are mentioned later, only the eccentric part 4c is demonstrated here. That is, the eccentric portion 4 c is provided eccentrically by a predetermined distance E from the axis of the rotating shaft 4 and is accommodated in the cylinder chamber 8.

An eccentric roller 15 is fitted on the circumferential surface of the eccentric portion 4c. The height dimension (axial length) H of the eccentric roller 15 is set to be the same as or slightly smaller than the height dimension of the cylinder chamber 8. Further, the ratio of the height dimension H of the eccentric roller 15 to the shaft diameter φD3 of the eccentric portion 4c is set to 0.8 or less (H / φD3 <0.8).
As will be described later, the eccentric portion 4c rotates eccentrically in the cylinder chamber 8 along with the rotation of the rotating shaft 4, and accordingly, a part of the peripheral surface of the eccentric roller 15 moves while contacting the peripheral surface of the cylinder chamber 8. It is like that.

  A blade chamber 17 is provided in the cylinder 7, and a blade 18 and a spring member 19 are accommodated in the blade chamber 17. The tip of the blade 18 is formed in a substantially semicircular shape in plan view, and is elastically pressed by the spring member 19 which is a compression spring so that the tip is in line contact with the circumferential surface of the eccentric roller 15 along the axial direction. The

  When the rotating shaft 4 rotates, the eccentric portion 4c rotates eccentrically, and the eccentric roller 15 moves along the circumferential surface of the cylinder chamber 8, the blade 18 is moved to the blade chamber 17 by the urging force of the eccentric roller 15 and the spring member 19. Reciprocate along. Therefore, regardless of the rotation angle of the eccentric roller 15, the tip of the blade 18 comes into contact with the circumferential surface of the eccentric roller 15 to partition the cylinder chamber 8 into two chambers.

  When the leading end of the blade 18 is at the most protruding portion into the cylinder chamber 8, the rear end of the blade 18 is located in the blade chamber 17. When the eccentric roller 15 is in close contact with the cylinder chamber 8 and the tip of the blade 18 and the blade 18 is most retracted, the distance between the rear end of the blade 18 and the end surface of the blade chamber 17 is slightly smaller than the maximum compression length of the spring member 19. Designed to be large.

  In the compression mechanism portion 2 configured as described above, most of the compression mechanism portion 2 is immersed in the lubricating oil of the oil reservoir 20 formed on the inner bottom portion of the sealed case 1. The lower end surface of the auxiliary shaft portion 4b is exposed from the auxiliary bearing 10 and the valve cover 13, and an oil supply pump is provided here. The rotary shaft 4 is provided with an oil supply passage communicating with the oil supply pump that branches from the sliding contact portions of the compression mechanism portion 2.

  As the sliding contact portion, for example, between the rotation shaft main shaft portion 4a and the main bearing 9, between the rotation shaft sub shaft portion 4b and the sub bearing 10, between the rotation shaft eccentric portion 4c and the eccentric roller 15, and the eccentric roller 15 And the cylinder chamber 8 circumferential surface. Lubricating oil in the oil reservoir 20 is pumped up by an oil pump accompanying the rotation of the rotating shaft 4 and guided to each sliding contact portion through an oil supply passage.

  The axial length of the eccentric portion 4c is smaller than the height dimension of the eccentric roller 15, and accordingly, there is a certain dimensional difference between the upper and lower end surfaces of the eccentric portion 4c and the upper and lower end surfaces of the eccentric roller 15. . The upper and lower end corners of the eccentric roller 15 are cut obliquely to form a chamfered portion Ma on which a so-called chamfering process is performed.

  Since there is a dimensional difference between the upper end of the eccentric part 4c and the upper end of the eccentric roller 15, and the lower end of the auxiliary escape part f is inserted into the inner diameter part of the eccentric roller 15, the auxiliary escape part f is opposite to the side where the eccentric part 4c is eccentric. Is formed obliquely from the main shaft portion 4a to the eccentric portion 4c. Since the chamfered portion Ma is provided at the inner diameter portion of the eccentric roller 15, the auxiliary escape portion f does not contact the upper end of the inner diameter portion of the eccentric roller 15.

  On the other hand, the axis of the connecting portion 4d and the axis of the sub-shaft portion 4b coincide with each other, and the shaft diameter of the connecting portion 4d is set smaller than the shaft diameter of the sub-shaft portion 4b. That is, the peripheral surface of the connecting portion 4d is stepped from the peripheral surface of the sub-shaft portion 4b, and a later-described escape portion (escape means) L is formed over the entire circumference. A so-called chamfering process is performed on the connecting corner portion of the auxiliary shaft portion 4b and the connecting portion 4d, which is the lower end of the escape portion L, to form a chamfered portion Mb.

  In this way, the main shaft portion 4a and the like are provided on the rotating shaft 4, and the recessed portion g is provided at a site along the axis of the auxiliary bearing 10 and facing the connecting portion 4d. The reason why the thickness of the flange portion 10b of the auxiliary bearing 10 is larger than the thickness of the flange portion 9b of the main bearing 9 is to provide the recessed portion g that accommodates the connecting portion 4d.

Below, the structure of the principal part in the compression mechanism part 2 is demonstrated.
When the shaft diameter of the main shaft portion 4a provided on the rotating shaft 4 is φD1, the shaft diameter of the auxiliary shaft portion 4b is φD2, the shaft diameter of the eccentric portion 4c is φD3, and the eccentric amount of the eccentric portion 4c is E (1) ) And (2).
φD3 <φD1 + 2 × E (1)
φD3 <φD2 + 2 × E (2)
The escape portion L is formed over the entire circumference of the connecting portion 4d, the axial length of the connecting portion 4b, which is the escape portion L, is Z, the height dimension (axial length) of the eccentric roller 15 is H, and eccentric. When the axial length of the chamfered portion Ma provided on the inner diameter portion of the roller 15 is Cr and the axial length of the chamfered portion Mb at the lower end of the escape portion L is Cf, the following formula (3) is set to be satisfied. Yes.
Z ≧ H-Cr-Cf (3)
Note that the sizes of the chamfered portions Ma and Mb include zero, and therefore, the chamfered portions Ma and Mb are also applied when no chamfered portions Ma and Mb exist.

Next, the operation of the rotary compressor and the refrigeration cycle apparatus configured as described above will be described.
When the motor unit 3 in the rotary compressor A is energized, the rotary shaft 4 is rotationally driven, and the eccentric roller 15 moves eccentrically in the cylinder chamber 8 constituting the compression mechanism unit 2. In the cylinder chamber 8, the refrigerant gas evaporated by the evaporator D and separated by the gas-liquid separator is sucked through the refrigerant pipe P into one chamber which is partitioned by the blade 18 and communicates with the refrigerant pipe P.

  When the eccentric roller 15 continues the eccentric movement, the volume of the chamber on the side where the refrigerant gas is sucked decreases, and the pressure increases. When the volume of the chamber reaches a predetermined volume, the compressed refrigerant gas rises to a predetermined pressure. At the same time, the discharge valve mechanisms provided in the main bearing 9 and the sub-bearing 10 are opened, and the refrigerant gas compressed to high temperature and pressure is discharged into the valve covers 12 and 13.

  The compressed refrigerant gas is led out from the valve covers 12 and 13 directly or indirectly to the space between the compression mechanism 2 and the electric motor 3 in the sealed case 1. The compressed refrigerant gas flows through the refrigerant gas flow passage provided in the electric motor unit 3 and fills the sealed case 1 on the upper side of the electric motor unit 3.

  The refrigerant gas is discharged to the refrigerant pipe P connected to the upper end of the rotary compressor A, led to the condenser B to be condensed and liquefied, led to the expansion device C and adiabatically expanded, and led to the evaporator D to evaporate. Then, it takes away the latent heat of vaporization from the surroundings and performs a freezing action. The evaporated refrigerant is guided to the gas-liquid separator to be gas-liquid separated, and only the gas component is guided from the gas-liquid separator to the rotary compressor A through the refrigerant pipe P.

  The refrigerant gas is guided to the cylinder chamber 8 through the suction passage of the cylinder 7 constituting the compression mechanism unit 2 of the rotary compressor A. When the eccentric roller 15 is moved eccentrically, it is compressed again and discharged from the discharge valve mechanism when it reaches a predetermined pressure. Thereafter, the above-described operation is repeated.

  On the other hand, as the rotary shaft 4 rotates, the oil supply pump sucks up the lubricating oil in the oil reservoir 20 and supplies it to the sliding contact portions such as between the rotary shaft 4 and the main bearing 9 through the oil supply passage. . In each sliding contact portion, a sufficient amount of lubricating oil is guided from the oil reservoir portion 20 to maintain lubricity. The lubricating oil supplied to each sliding contact portion is collected again in the original oil reservoir 20.

  In the rotary compressor A, it is desirable to reduce the diameter of the eccentric portion 4c having the largest diameter at the sliding portion of the rotating shaft 4 as much as possible in order to reduce friction loss and improve efficiency. Accordingly, the thickness of the cylinder 7 may be further reduced, and the eccentric amount of the eccentric portion 4c may be increased to reduce the sliding loss of the rotating shaft 4.

As described above, when the shaft diameter φD1 of the main shaft portion 4a, the shaft diameter φD2 of the auxiliary shaft portion 4b, the shaft diameter φD3 of the eccentric portion 4c, and the eccentric amount E of the eccentric portion 4c, the following equations (1) and (2) It is set to satisfy the formula.
φD3 <φD1 + 2 × E (1)
φD3 <φD2 + 2 × E (2)
Thus, even if the eccentric amount of the eccentric portion 4c is large, the shaft diameter φD1 of the main shaft portion 4a that is rotatably fitted to the main bearing 9 and the shaft diameter of the sub shaft portion 4b that is rotatably fitted to the sub bearing 10 The diameter of the eccentric portion 4c can be reduced without reducing φD2.

  Therefore, while maintaining the shaft reliability of the main shaft portion 4a and the sub shaft portion 4b of the rotary shaft 4 with respect to the main bearing 9 and the sub bearing 10, the sliding diameter of the eccentric portion 4c can be reduced and the sliding loss can be reduced. A rotary compressor A having high performance and high performance is obtained. And the refrigerating-cycle apparatus which comprises this rotary compressor A and comprises a refrigerating cycle can obtain the improvement of refrigerating efficiency.

  Furthermore, since the ratio of the height dimension H of the eccentric roller 15 and the shaft diameter φD3 of the eccentric portion 4c is set to 0.8 or less (H / φD3 <0.8), the height dimension H of the eccentric roller 15 is set to The distance between the main shaft portion 4a and the sub shaft portion 4b can be shortened to improve the reliability by reducing the amount of deflection of the rotating shaft 4, and to reduce noise and vibration, and to reduce the size of the rotary compressor A. Is possible.

When the eccentric roller 15 is assembled to the eccentric portion 4c of the rotating shaft 4, a connecting portion 4d having the entire circumference as a relief portion L is provided on the side of the auxiliary shaft portion 4b, the axial length Z of the relief portion L, the height of the eccentric roller 15 When the height dimension H, the axial length Cr of the chamfered portion Ma, and the axial length Cf of the chamfered portion Mb are set, the equation (3) is set to be satisfied.
Z ≧ H-Cr-Cf (3)
From the above settings, the eccentric roller 15 can be inserted from the end surface side of the sub-shaft portion 4b, and can be easily assembled to the eccentric portion 4c via the connecting portion 4d, and the assembly workability of the eccentric roller 15 with respect to the eccentric portion 4c can be improved. it can.
In other words, it is possible to insert the inner diameter portion of the eccentric roller 15 from the end surface of the main shaft portion 4a. However, even if the insertion side end surface of the eccentric roller 15 abuts on the end surface of the eccentric portion 4c, most of the eccentric roller 15 is inserted. Is still inserted in the main shaft portion 4a, and the eccentric roller 15 cannot be moved in the radial direction from that position.

  On the other hand, in this embodiment, a connecting portion 4d is provided between the auxiliary shaft portion 4b and the eccentric portion 4c. Therefore, the eccentric roller 15 is inserted from the end surface side of the sub shaft portion 4b, reaches the connecting portion 4d through the sub shaft portion 4b, and at the position where the eccentric roller 15 and the connecting portion 4d face each other correctly, the eccentric roller 15 is moved to the eccentric portion. It moves in the eccentric direction of 4c.

  That is, the eccentric roller 15 is brought into contact with the escape portion L, and the eccentric roller 15 is correctly opposed to the circumferential surface of the eccentric portion 4c, and then the eccentric roller 15 is moved along the axial direction. It fits into the part 4c.

  Since the chamfered portion Ma is provided in the eccentric roller 15 and the chamfered portion Mb is provided in the counter shaft portion 4b, the upper and lower ends of the inner diameter portion of the eccentric roller 15 are the upper and lower ends of the connecting portion 4d and the eccentric portion 4c. The eccentric roller 15 can be smoothly inserted into the eccentric portion 4c without being caught by the eccentric portion 4c.

  The auxiliary shaft portion 4b is brought closer to the eccentric portion 4c, and the distance between the main shaft portion 4a and the auxiliary shaft portion 4b is reduced. As a result, the amount of deflection of the rotating shaft 4 can be reduced during actual compression operation, and reliability can be improved and vibration and noise can be reduced, leading to a reduction in the size of the rotary compressor A itself.

  The basic structure of the compression mechanism part 2 constituting the rotary compressor A is as described above, and it is premised that the compression mechanism part 2 is not changed, and considering the improvement in workability when the eccentric roller 15 is assembled to the eccentric part 4c, The following embodiments are possible. That is, on the premise of the relationship of H / φD3 <0.8 and the above equations (1) and (2), the structure of the relief portion L and the setting as described below instead of the above equation (3) It may be.

FIG. 2A is a partial cross-sectional view of the rotary compressor A according to the second embodiment, and FIG. 2B is a cross-sectional view taken along the line SS of FIG. 2A. (The same components as those in FIG. 1 are denoted by the same reference numerals and new description is omitted.)
As shown in FIG. 2A, the axial length of the connecting portion 4d1 provided between the auxiliary shaft portion 4b and the eccentric portion 4c is extremely short, and the shaft diameter is slightly smaller than the auxiliary shaft portion shaft diameter φD2. It is formed. An escape portion (escape means) 22 is provided in the range of length Za from the end surface on the eccentric portion 4c side of the connecting portion 4d1 to the end surface side of the auxiliary shaft portion 4b.

  As shown in FIG. 2B, the escape portion 22 is centered on the center position Oa of the eccentric portion 4c, and a part of the peripheral surface opposite to the eccentric direction of the eccentric portion 4c is the same as the peripheral surface of the eccentric portion 4c. It is formed by cutting with a curvature radius that becomes a surface. The range (angle θ) in which the relief portion 22 is provided is 120 ° or less from the center Ob of the auxiliary shaft portion 4b.

  In addition, although the above-mentioned clearance part 22 peripheral surface may be processed so that it may be located inside the peripheral surface of the eccentric part 4c, at least the relief part peripheral surface that protrudes outward from the peripheral part 4c peripheral surface Should not be.

  As shown in FIG. 2A again, the corner of the lower end of the escape portion 22 (the lower end side of the auxiliary shaft portion 4b) is a chamfered portion Mc that has been chamfered. There is no change in that the chamfered portion Mb is provided at the upper end corner portion of the auxiliary shaft portion 4b provided continuously with the connecting portion 4d1, and the chamfered portion Ma is also provided at the upper and lower ends of the inner diameter portion of the eccentric roller 15.

The axial length of the escape portion 22 is Za, the height of the eccentric roller 15 is H, the axial length of the chamfered portion Ma of the inner diameter portion of the eccentric roller 15 is Cr, and the axial length of the chamfered portion Mc of the escape portion 22. Is set so that the following expression (4) is satisfied.
Za ≧ H—Cr—Cg (4)
When the eccentric roller 15 is assembled, the inner diameter portion of the eccentric roller 15 is inserted from the end surface side of the auxiliary shaft portion 4b, and the eccentric roller 15 is correctly opposed to the escape portion 22. Then, the eccentric roller 15 is translated in the eccentric direction of the eccentric portion 4c, and a part of the inner diameter portion of the eccentric roller 15 is brought into contact with the circumferential surface of the escape portion 22. In this state, the eccentric roller 15 is moved along the axial direction and fitted into the eccentric portion 4c.

  At this time, since the equation (4) is set and the chamfered portion Ma is provided on the eccentric roller 15 and the chamfered portion Mc is provided on the escape portion 22, the upper and lower end portions of the inner diameter portion of the eccentric roller 15 are located on the escape portion 22. The eccentric roller 15 can be smoothly opposed and fitted into the eccentric portion 4c without being caught by the upper and lower end portions and the end portions of the eccentric portion 4c.

  The auxiliary shaft portion 4b further approaches the eccentric portion 4c, and the distance between the main shaft portion 4a and the auxiliary shaft portion 4b is further shortened than that described in the first embodiment. Therefore, the amount of deflection of the rotating shaft 4 can be further reduced, and the reliability can be further improved and the vibration and noise can be further reduced, which leads to the miniaturization of the rotary compressor A itself.

  Since the center of the escape portion 22 is substantially the same as the position of the center Oa of the eccentric portion 4c, the escape portion 22 can be processed coaxially with the eccentric portion 4c, and the productivity is improved. Since the escape portion 22 is provided in a range of 120 ° or less from the center Ob, the shaft areas of the auxiliary shaft portion 4b and the connecting portion 4d1 that receive the axial load force can be sufficiently secured, and the shaft reliability is not impaired.

Next, the third embodiment will be described assuming that the preconditions in the second embodiment are the same (the same applies to the following embodiments).
3A is a partial cross-sectional view of the rotary compressor A according to the third embodiment, and FIG. 3B is a transverse cross-sectional view taken along the line TT in FIG. 3A.
As shown in FIG. 3A, the axial length Zb of the connecting portion 4d2 provided between the auxiliary shaft portion 4b and the eccentric portion 4c is extremely short, and the shaft diameter is slightly smaller than the auxiliary shaft portion 4b shaft diameter φD2. It is formed small. Further, a roller escape portion 24 is provided on the peripheral surface of the connecting portion 4d2 opposite to the eccentric direction of the eccentric portion 4c.

  The roller escape portion 24 is provided over the entire length of the connecting portion 4d2 in the axial direction. Therefore, the axial length of the roller escape portion 24 is Zb. In particular, as shown in FIG. 3B, the center position Oa of the roller escape portion 24 is different from the center position Ob of the connecting portion 4d2, and is at a position coincident with the center Oa of the eccentric portion 4c.

  The roller escape portion 24 forms the same curved surface as a part of the peripheral surface of the eccentric portion 4c, and is in a continuous state. The range (angle: θ) in which the roller escape portion 24 is provided is also about 120 ° or less here.

  On the other hand, a counter shaft escape portion 25 is provided in the inner diameter portion of the eccentric roller 15 from the lower end surface to a predetermined length B. The auxiliary shaft relief portion 25 is recessed with the same radius of curvature as the peripheral surface of the auxiliary shaft portion 4b. Alternatively, the radius of curvature may be larger, and it should not be at least a radius of curvature smaller than the same radius of curvature.

  As a result, the countershaft relief portion 25 is formed on the same surface as the peripheral surface of the subshaft portion 4b, or a surface positioned on the outer side of the peripheral surface of the subshaft portion 4. In addition, it is the same that the range (angle: θ) in which the auxiliary shaft relief portion 25 is provided is about 120 ° or less. In particular, the corner portion on the upper end side of the countershaft relief portion 25 is a chamfered portion Md to be chamfered.

The axial length of the connecting portion 4d2 is Zb, the height dimension of the eccentric roller 15 is H, the axial length of the auxiliary shaft escape portion 25 is B, and the axial length of the chamfered portion Md of the auxiliary shaft escape portion 25 is the axial length. When Ch is the axial length Cf of the chamfered portion Mb of the roller escape portion 24, the following equation (5) is satisfied.
Zb ≧ (H−B) Ch−Cf (5)
From the above setting, the inner diameter portion of the eccentric roller 15 is inserted from the end surface side of the auxiliary shaft portion 4b, and when the upper end portion of the eccentric roller 15 faces the connecting portion 4d2, the roller escape portion 24 of the connecting portion 4d2 and the auxiliary roller 15 of the eccentric roller 15 become auxiliary. The eccentric roller 15 is rotated and adjusted in the circumferential direction so as to face the shaft escape portion 25.

  Then, the eccentric roller 15 is moved in the eccentric direction of the eccentric portion 4c, the auxiliary shaft escape portion 25 of the eccentric roller 15 is brought into close contact with a part of the peripheral surface of the auxiliary shaft portion 4b, and the upper portion from the auxiliary shaft escape portion 25 is connected to the connecting portion. The roller escape portion 24 of 4d2 is in close contact. In this state, the eccentric roller 15 is moved along the axial direction of the eccentric portion 4c, and is fitted into the eccentric portion 4c.

  At this time, since the formula (5) is set, the inner diameter portion of the eccentric roller 15 is not caught by the eccentric portion 4c, and the eccentric roller 15 can be smoothly opposed to the eccentric portion 4c. Moreover, since the upper and lower end portions of the inner diameter portion of the eccentric roller 15 are the chamfered portions Ma, the inner diameter portion of the eccentric roller 15 can be more smoothly opposed to the eccentric portion 4c.

  Therefore, like the configuration described above, the auxiliary shaft portion 4b is further brought closer to the eccentric portion 4c, and the distance between the main shaft portion 4a and the auxiliary shaft portion 4b is further shortened. Therefore, the amount of bending of the rotating shaft 4 can be further reduced, reliability can be improved, vibration and noise can be further reduced, and the rotary compressor A itself can be further downsized.

  Since the center of the roller escape portion 24 is substantially the same as the position of the eccentric portion 4c center Oa, the roller escape portion 24 can be processed coaxially with the eccentric portion 4c, and the productivity is improved. Since the auxiliary shaft relief portion 25 is provided within a range of 120 ° or less from the center portion Oa of the eccentric portion 4c, even if the eccentric portion 4c receives the axial load force via the eccentric roller 15, a sufficient shaft area can be secured and the shaft reliability can be secured. Will not be damaged.

FIGS. 4A and 4B are partial plan views of the rotary compressor A illustrating the fourth embodiment, which are different from each other.
FIG. 4A includes a so-called swing type compression mechanism 2A in which the eccentric roller 15 and the blade 18a are integrally formed. By providing this type of structure, the rotation of the eccentric roller 15 can be reliably restricted, and only the eccentric motion can be performed, so that the compression efficiency can be improved.

Also in this case, as described above with reference to FIGS. 3A and 3B, the connecting portion 4d2 is provided between the auxiliary shaft portion 4b and the eccentric portion 4c, and the roller escape portion 24 is provided in the connecting portion 4d2. Provide. The eccentric roller 15 to which the blade 18a is integrally connected is provided with a countershaft relief portion 25.
The eccentric roller 15 is inserted from the end surface side of the auxiliary shaft portion 4b, and when the portion above the auxiliary shaft escape portion 24 of the inner diameter portion of the eccentric roller 15 faces the connection portion 4d2, the roller escape portion 24 of the connection portion 4d2 and the eccentric roller 15 The eccentric roller 15 is rotated and adjusted in the circumferential direction so that the countershaft relief portion 25 of the countershaft faces the straight shaft.

  Further, the eccentric roller 15 is moved in the eccentric direction of the eccentric portion 4c so that the auxiliary shaft escape portion 24 of the eccentric roller 15 is in close contact with a part of the peripheral surface of the auxiliary shaft portion 4b, and the inner diameter extending from the auxiliary shaft escape portion 25 to the upper end surface. The portion is brought into close contact with the roller escape portion 24. Then, the eccentric roller 15 is moved along the axial direction and is fitted into the eccentric portion 4c.

  That is, there is no change in the assembly of the eccentric roller 15 with the blade 18a integrated with the eccentric portion 4c, but the auxiliary shaft relief portion 25 of the eccentric roller 15 and the roller relief portion 24 of the connecting portion 4d2 are cylinders as shown in the figure. 7 is provided on the gas suction passage 28 side. Reference numeral 29 denotes a discharge port provided to face the discharge valve mechanism.

  Accordingly, since the cylinder chamber 8 is partitioned into the suction chamber m and the compression chamber n by the blade 18a during the actual compression action, the suction chamber m is provided with 25 countershaft relief portions. The axial load force is hardly applied to the portion 4c, and the shaft reliability of the eccentric portion 4c is not impaired.

  FIG. 4B shows a so-called hinged structure in which a concave portion 15a formed in a concave shape is provided along the peripheral surface with which the blade 18 of the eccentric roller 15 contacts, and the blade 18 whose tip is formed in an arc shape is brought into contact with the concave portion 15a. A compression mechanism 2B called a blade type is provided. Similar to the swing type of FIG. 4A, the eccentric roller 15 can be restrained from rotating so that only the eccentric motion is performed, and the compression efficiency can be improved.

  Also in this case, the roller escape portion 24 of the connecting portion 4d2 and the counter shaft escape portion 25 of the eccentric roller 15 are provided on the suction chamber m side. Therefore, almost no axial load force is applied to the eccentric portion 4c via the eccentric roller 15, and the shaft reliability of the eccentric portion 4c is not impaired.

  FIG. 5 is a partial cross-sectional view of a rotary compressor A for explaining the fifth embodiment. A roller escape portion 24a is provided across a part of the countershaft portion 4b and the entire connecting portion 4d2. Further, a counter shaft escape portion 25a is provided from the lower end of the inner diameter portion of the eccentric roller 15 to the middle portion on the upper end side.

  The roller escape portion 24 described above with reference to FIG. 3 (A) is not provided only in the connecting portion 4d2, but the roller escape portion 24a is extended toward the auxiliary shaft portion 4b, and the auxiliary shaft provided in the eccentric roller 15 correspondingly. This is a configuration in which the length of the escape portion 25a is shortened, and is basically the same as that of the second embodiment, and therefore the same effect can be obtained.

  FIG. 6 is a partial cross-sectional view of a multi-cylinder rotary compressor Aa illustrating a sixth embodiment. The compression mechanism portion 2C connected to the electric motor portion 3 via the rotary shaft 4 includes a frame 9A in which a main bearing portion is integrally provided, and two cylinders 7A and 7B each having a cylinder chamber 8 are provided with an intermediate partition plate 30. Mounted through.

  Even in this case, on the premise that the relationship of the height dimension H of the eccentric roller 15 / the shaft diameter φD3 <0.8 of the eccentric portion 4c and the expressions (1) and (2) described above are satisfied. As described previously in the second embodiment (FIG. 2), the escape portion 22 is provided across the auxiliary shaft portion 4b and the connecting portion 4d. Although not shown in particular, the above formula (4) is established by providing chamfered portions on the inner diameter portion of the eccentric roller 15 and the escape portion 22.

  The eccentric roller 15 previously inserted from the end surface side of the auxiliary shaft portion 4b can be fitted into the lower-side eccentric portion 4c using the escape portion 22, and further fitted into the upper-side eccentric portion 4c via the intermediate connecting portion 31. The eccentric roller 15 inserted into the auxiliary shaft portion 4b afterwards can be fitted into the eccentric portion 4c on the lower side.

  Therefore, even in the multi-cylinder rotary compressor Aa, each eccentric roller 15 can be fitted into the eccentric portion 4c without changing from the single cylinder rotary compressor A, and the same action as described above can be achieved. An effect will be acquired.

  In the first to sixth embodiments, the eccentric roller 15 is inserted from the end surface side of the auxiliary shaft portion 4b and fitted into the eccentric portion 4c. However, the present invention is not limited to this. Alternatively, the eccentric roller 15 may be inserted from the end surface on the main shaft portion 4a side and fitted into the eccentric portion 4c. In this case, all of the clearance part and the related matters are changed from the auxiliary shaft part 4b side to the main shaft part 4a side.

  In the second to sixth embodiments, the ratio of the height dimension H of the eccentric roller 15 and the shaft diameter φD3 of the eccentric portion 4c is 0.8 or less (H / φD3 <0.8). The height H of the eccentric roller 15 can be reduced, the distance between the main shaft portion 4a and the sub shaft portion 4b can be shortened, reliability can be improved by reducing the amount of deflection of the rotating shaft 4, and noise / Vibration can be reduced, and the rotary compressor A (multi-cylinder rotary compressor Aa) can be downsized.

  Furthermore, the present invention is not limited to the above-described embodiments as they are, and can be embodied by modifying the constituent elements without departing from the scope of the invention in the implementation stage. Various inventions can be formed by appropriately combining a plurality of constituent elements disclosed in the above-described embodiments.

The longitudinal cross-sectional view of the rotary compressor based on 1st Embodiment in this invention, and the refrigerating cycle block diagram of an air conditioner. The partial longitudinal cross-sectional view of the rotary compressor based on the said 2nd Embodiment, and the cross-sectional view which follows an SS line. The partial longitudinal cross-sectional view of the rotary compressor based on the said 3rd Embodiment, and the cross-sectional view which follows a TT line. The partial top view of a mutually different structure based on the said 4th Embodiment. The partial longitudinal cross-sectional view of the rotary compressor based on the said 5th Embodiment. The partial longitudinal cross-sectional view of the multi-cylinder rotary compressor based on the said 6th Embodiment.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 9 ... Main bearing, 4a ... Main shaft part, 10 ... Sub bearing, 4b ... Sub shaft part, 15 ... Eccentric roller, 4c ... Eccentric part, 4 ... Rotating shaft, 8 ... Cylinder chamber, 7 ... Cylinder, L ... Escape part, DESCRIPTION OF SYMBOLS 22 ... Escape part, 24 ... Roller escape part, 25 ... Secondary shaft escape part, A ... Rotary compressor, B ... Condenser, C ... Expansion device, D ... Evaporator.

Claims (4)

A rotary shaft having a main shaft portion pivotally supported by the main bearing, a subshaft portion pivotally supported by the sub-bearing, and an eccentric portion which is eccentrically provided between the main shaft portion and the sub-shaft portion and engages with the roller. When,
A rotary compressor that includes the cylinder that houses the roller that engages with the eccentric portion of the rotating shaft and includes a cylinder chamber in which the roller moves eccentrically while contacting the peripheral surface as the rotating shaft rotates. ,
When the shaft diameter of the main shaft portion of the rotating shaft is φD1, the shaft diameter of the auxiliary shaft portion is φD2, the shaft diameter of the eccentric portion is φD3, and the amount of eccentricity of the eccentric portion is E,
φD3 <φD1 + 2 × E (1)
φD3 <φD2 + 2 × E (2)
In order to satisfy the expressions (1) and (2),
At least one of the main shaft portion and the sub shaft portion of the rotating shaft or the roller is provided with a relief means when the roller is assembled to the eccentric portion via the main shaft portion or the sub shaft portion. And rotary compressor.   The escape means is either the main shaft portion or the sub-shaft portion of the rotating shaft, and on the opposite side opposite to the eccentric direction of the eccentric portion, is the same as the eccentric portion peripheral surface or the eccentric portion circumference. The rotary compressor according to claim 1, wherein the rotary compressor is provided so as to be located inside the surface.   The escape means is provided at the inner diameter portion of the roller so as to be located on the same or the outer peripheral surface of the shaft portion of either the main shaft portion or the sub shaft portion. The rotary compressor according to claim 1.   A refrigeration cycle apparatus comprising the rotary compressor according to claim 1, a condenser, an expansion device, and an evaporator to constitute a refrigeration cycle.

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