JP4733558B2 - Fluid machinery and refrigeration cycle equipment - Google Patents

Description

  The present invention relates to a fluid machine including a rolling piston compressor and an expander in which a roller and a blade are integrated parts, and a refrigeration cycle apparatus including the fluid machine.

  For example, in a fluid machine such as an expander or a rolling piston compressor, a cylinder, a roller incorporated in the cylinder, and a crank portion provided on a rotating shaft and engaged with the roller each have a component accuracy such as a squareness. It is manufactured to be within the tolerance range. Therefore, strictly speaking, these components are assembled with a certain inclination within the predetermined tolerance range. The inclination is corrected by the large clearance between the parts with respect to the inclination between the parts.

  The larger the clearance between the component parts, the larger the correction amount, and the greater the margin for manufacturing and assembling the parts. On the other hand, if the clearance is too large, it will cause a gas leak and reduce the performance, so it is necessary to keep it below a certain value. However, if the accuracy of the parts such as the squareness deteriorates to a level that is large with respect to the clearance, the inclination cannot be corrected, and it may cause wear due to part contact due to the inclination of the part.

  In the rolling piston compressor, a roller and a blade are generally configured as separate parts. The blade is pressed against the roller by back pressure or a spring, and slides against the roller. In this case, since the roller and the blade have a degree of freedom of inclination as independent parts, there is little problem with respect to the allowable inclination angle.

On the other hand, for example, in a rolling piston compressor disclosed in [Patent Document 1] and [Patent Document 2], a roller and a blade are configured as an integral part. The blade is also referred to as a swing-type rotary compressor because the blade is oscillated between two semicylindrical oscillating bushes provided in the cylinder.
JP-A-6-58276 JP-A-6-317279

  Such a compressor has advantages such as a reduction in friction loss and leakage between the roller and the blade because sliding between the roller and the blade is eliminated as compared with a general compressor in which the roller and the blade are separated. On the other hand, the distance from the roller center to the blade tip surface becomes longer, and the inclination angle of the parts at the time of assembling is restricted, so that the precision of the parts such as the squareness is required more strictly.

  If it demonstrates, as shown in FIG. 8, the crank part d integrally provided in a rotating shaft will be accommodated in the cylinder chamber b formed in the internal diameter part of the cylinder a. A roller g is fitted in the crank part d, and the roller g and the blade f are provided as separate parts so that the blade f contacts the outer peripheral surface of the roller g, or the roller g and the blade f are integrally formed. The

  In such a structure, there is a radial clearance between the outer peripheral surface of the roller g and the peripheral surface of the cylinder chamber b, and there is a radial clearance between the inner peripheral surface of the roller g and the peripheral surface of the crank part d. Further, there is a height direction clearance C between a height direction that is a direction along the central axis of the roller g and a height direction that is a direction along the central axis of the cylinder a.

In the following, the allowable inclination angle α in a general structure in which the roller g and the blade f are separate parts and are in sliding contact with each other, and as shown in the above-mentioned [Patent Publication 1] and [Patent Publication 2], the roller g And the allowable inclination angle β in the structure in which the blade f is integrated.
As shown in FIG. 9, in a general structure in which the roller g and the blade f are separate parts, the allowable inclination angle is C, where the clearance in the height direction of the roller g with respect to the cylinder a is C and the outer radius of the roller g is R. α is tan ⁻¹ (C / R).

As shown in FIG. 10, in the structure in which the roller g and the blade f are integrated, the clearance in the height direction of the roller g with respect to the cylinder a is C, and the distance from the center of the roller g to the tip surface of the blade f is L. The allowable inclination angle β is tan ⁻¹ (C / L).
As described above, the allowable inclination angle β of the structure in which the roller g and the blade f shown in FIG. 10 are integrated is larger than the allowable inclination angle α of a general structure in which the roller g and the blade f shown in FIG. Small (β <α). For this reason, there has been a problem that the blade tip and the like are more likely to be worn by one piece due to the inclination of the roller / blade integrated component due to component accuracy and the like.

  The present invention has been made based on the above circumstances, and the object of the present invention is a structure in which a roller and a blade are integrated to prevent contact with each other due to the inclination of the component, and to improve the component accuracy and the assembly accuracy. It is an object of the present invention to provide a fluid machine that can increase the margin of the refrigeration and that can improve the productivity, and a refrigeration cycle apparatus that can improve the refrigeration efficiency by including the fluid machine.

  In order to satisfy the above object, a fluid machine according to the present invention includes a cylinder provided with a cylinder chamber, a rotary shaft provided through the cylinder chamber of the cylinder and having a crank portion at a portion facing the cylinder chamber, and the rotation A roller that engages with the crank portion of the shaft and makes an eccentric revolving motion in the cylinder chamber as the rotating shaft rotates, and is provided integrally with this roller and swings along with the eccentric revolving motion of the roller to compress the cylinder chamber into the compression portion And a blade partitioned into a suction portion, and a ball bearing interposed between the crank portion of the rotating shaft and the roller, and the distance L from the center of the roller to the tip surface of the blade is defined as the outer peripheral radius R of the roller. 2 or less (L <2R).

  Furthermore, in order to satisfy the above object, the refrigeration cycle apparatus of the present invention includes a compressor as the fluid machine, a condenser, the compressor, a condenser, an expansion device, and an evaporator.

  According to the present invention, a fluid machine capable of reliably preventing one-sided contact due to the inclination of a roller / blade integrated component, improving the accuracy of the component, expanding the margin of assembly accuracy, and improving productivity. A refrigeration cycle apparatus that is provided with this fluid machine and that can improve the refrigeration efficiency can be provided.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. (Note that components not marked in the text are not shown)
FIG. 1 is a partial longitudinal sectional view of a rolling piston compressor (hereinafter simply referred to as a “compressor”) S, which is a fluid machine according to a first embodiment, and a refrigeration cycle apparatus including the compressor S. It is a refrigeration cycle block diagram.

  First, the refrigeration cycle apparatus will be described. In the figure, S is a compressor, and a refrigerant pipe P projects from the upper end surface of the compressor S. Condenser 1, expansion device 2, and evaporator 3 are sequentially communicated with refrigerant pipe P, and a gas-liquid separator is provided in the middle of refrigerant pipe P extending from evaporator 3. The end of the pipe P is connected to the side surface of the compressor S. These constitute the refrigeration cycle circuit K.

  Next, the compressor S will be described. The compressor S includes a sealed case 5. A compression mechanism 6 is accommodated in the lower part of the sealed case 5, and an electric motor part 7 is provided on the upper part of the compression mechanism 6. The electric motor unit 7 and the compression mechanism unit 6 are connected to each other via a rotating shaft 8. A lubricating oil reservoir 9 is formed on the inner bottom of the sealed case 5, and a part of the compression mechanism 6 is immersed in the lubricating oil.

  The electric motor unit 7 includes a stator 10 fixed to the inner surface of the sealed case 5, and a rotor 11 that is disposed inside the stator 10 with a predetermined gap and is fitted to the rotary shaft 8. The The electric motor unit 7 is connected to an inverter that varies the operating frequency, and is electrically connected to a control unit that controls the inverter circuit via the inverter.

FIG. 2 is a partial cross-sectional plan view of the compression mechanism unit 6. Hereinafter, the compression mechanism 6 will be described in detail with reference to FIG.
The compression mechanism unit 6 includes a cylinder 13. The cylinder 13 is formed with a predetermined height along the central axis, and the outer diameter is slightly larger than the inner diameter of the sealed case 5. The cylinder 13 is pressed into the circumferential surface of the sealed case 5 and positioned and fixed by welding from the outside of the sealed case 5.

  A main bearing 14 is superimposed on the upper surface of the cylinder 13 and is fixed to the cylinder 13 together with an upper valve cover 15 via a mounting bolt 16. A sub-bearing 17 is superimposed on the lower surface portion of the cylinder 13, and is fixed to the cylinder 13 via a mounting bolt 19 together with a lower valve cover 18.

  The rotary shaft 8 has an intermediate portion protruding downward from the electric motor portion 7 rotatably supported by the main bearing 14 and a lower end portion rotatably supported by the auxiliary bearing 17. Further, the rotary shaft 8 penetrates through the inside of the cylinder 13, and a crank portion 8 a having a central axis that is eccentric from the central axis of the rotary shaft 8 by a predetermined dimension e is integrally provided in this penetrating portion.

  The upper and lower surfaces of the inner diameter portion of the cylinder 13 are closed by the main bearing 14 and the auxiliary bearing 17 to form a cylinder chamber 20. The crank portion 8 a of the rotating shaft 8 is in a position to be accommodated in the cylinder chamber 20. A discharge port provided with a discharge valve is provided at a portion of the main bearing 14 and the auxiliary bearing 17 facing the cylinder chamber 20 and covered with the upper and lower valve covers 15 and 18.

Also, a suction port 21 is provided through the cylinder 13 from the sealed case 5 and facing the open end of the cylinder chamber 20. The end of the refrigerant pipe P extending from the evaporator 3 is inserted into the suction port 21 and is firmly fixed.
On the other hand, the inner diameter portion of the ball bearing 22 is fitted into the rotary shaft crank portion 8a. A roller 23 constituting a swing member Y described later is fitted into the outer diameter portion of the ball bearing 22. In other words, the ball bearing 22 is interposed between the rotary shaft crank portion 8 a and the roller 23.

  The roller 23 has a ring shape made of a metal material, and the length (height) dimension along the central axis is somewhat to the length (height) dimension along the central axis of the cylinder chamber 20. Designed to form a clearance. A part of the outer peripheral surface of the roller 23 is provided in contact with a part of the peripheral surface of the cylinder chamber 20 along the central axis direction.

  As will be described later, during the compression operation, as the rotary shaft 8 is driven to rotate and the crank portion 8a rotates eccentrically, the roller 23 attached to the crank portion 8a via the ball bearing 22 moves eccentrically in the cylinder chamber 20. Make. In this state, the outer peripheral surface of the roller 23 and the peripheral surface of the cylinder chamber 20 are always in line contact with each other regardless of the rotation angle of the crank portion 8a.

3 is a plan view of the swing member Y and the ball bearing 22, FIG. 4 is a cross-sectional view of the swing member Y and the ball bearing 22, and FIG. 5 shows the dimensions of the components housed in the cylinder 13 and the cylinder chamber 20. It is sectional drawing to represent.
The oscillating member Y will be described. The oscillating member Y includes the roller 23 described above and a blade 25 attached to a part of the outer peripheral surface of the roller 23 with a fixing screw 24 and integrated with the roller 23. Composed.

The roller 23 is a ring-shaped member having a uniform thickness in the circumferential direction, whereas the blade 25 is a plate-shaped member formed with a predetermined plate thickness. The length in the height direction of the blade 25 coincides with the axial length of the roller 23.
The base end surface, which is the roller 23 side end surface of the blade 25, is formed in the same curved surface as the radius of curvature of the roller 23 outer peripheral surface, and is in close contact with the roller 23 outer peripheral surface. The tip surface which is the other end surface of the blade 25 forms a plane perpendicular to the height direction surface and the plate thickness direction surface.

  The length of the blade 25 and the roller 23 in the same direction with respect to the height direction of the cylinder chamber 20 is slightly shorter, and a clearance is secured in the height direction. The distance L from the center of the roller 23 to the tip surface of the blade 25 is set to be equal to or less than twice the outer radius R of the roller 23 (L <2R).

  On the other hand, a mounting hole 26 is provided penetrating from the base end surface of the blade 25 to the front end surface. In other words, the mounting hole 26 is provided through the longitudinal direction perpendicular to the height direction of the blade 25. The roller 23 is provided with a screw hole 27 along the radial direction between the outer peripheral surface and the inner peripheral surface.

  At the time of assembly, the base end portion of the blade 25 is temporarily held by contacting the outer peripheral surface of the roller 23 so that the mounting hole 26 of the blade 25 communicates with the screw hole 27 of the roller 23. The fixing screw 24 is inserted into the mounting hole 26. The blade 25 can be integrally attached and fixed to the roller 23 via the fixing screw 24 by projecting the distal end of the fixing screw 24 from the base end surface of the blade 25 and screwing it into the screw hole 27 provided in the roller 23.

  The tip of the blade 25 is housed in a swingable manner in a bush housing 30 adjacent to the cylinder chamber 20 in the cylinder 13 site. A relief space 31 is connected to a portion of the bush housing 30 opposite to the cylinder chamber 20 so that the tip of the blade 25 and the fixing screw 24 can be moved forward and backward as the blade 25 swings.

  The bush housing 30 includes a circular vertical hole 32 having a diameter much smaller than the diameter of the cylinder chamber 20 and a central axis parallel to the central axis of the cylinder chamber 20. However, it does not form a perfect circle, and a part of the cylinder chamber 20 is formed to communicate with each other with a predetermined width.

A width dimension communicating with the cylinder chamber 20 is secured in the vertical hole portion 32 as a space portion, and a pair of bushes 33 are fitted into the remaining portion. The blade 25 constituting the rocking member Y is inserted into the gap between the pair of bushes 33 constituting the bush housing 30.
The escape space 31 is a circular vertical hole having a smaller diameter than the vertical hole 32 and having a central axis parallel to the central axis of the cylinder chamber 20 and the vertical hole 32. As in the relationship between the vertical hole portion 32 of the bush housing portion 30 and the cylinder chamber 20, a part of the escape space portion 31 is connected to the vertical hole portion 32 with a predetermined width dimension.

  Oil grooves 35 are provided along the longitudinal direction on the thrust surfaces which are the upper and lower surfaces of the blade 25 in the height direction. An oil groove 36 is provided along the radial direction on the thrust surface, which is the upper and lower surfaces of the roller 23 in the height direction. In the state where the blade 25 and the roller 23 are integrally combined, the oil grooves 35 and 36 provided in the blade 25 and the roller 23 communicate with each other.

  In particular, as shown in FIG. 1, an oil escape passage 37 is provided through the upper and lower surfaces of the main bearing 14 portion facing the escape space portion 31 and the upper valve cover 15. Therefore, the escape space 31 communicates with the bush housing 30, while communicating with the inside of the sealed case 5 via the oil escape passage 37.

Next, the operation of the refrigeration cycle apparatus provided with the above-described compressor S will be described.
When the operation button on the operation panel is pressed, the control unit sends an operation signal to the motor unit 7 through the inverter. The rotating shaft 8 is driven to rotate, and the crank portion 8 a rotates eccentrically in the cylinder chamber 20. The roller 23 of the swing member Y fitted to the crank portion 8 a via the ball bearing 22 performs an eccentric revolving motion in the cylinder chamber 20.

  Specifically, when the roller 23 moves according to the eccentric rotation angle of the crank portion 8a, the angle of the blade 25 with respect to the bush housing portion 30 changes, and the pair of bushes 33 rotate in the vertical hole portion 32. The blade 25 swings while reciprocating along the bush housing 30.

  In this state, the blade 25 divides the inside of the cylinder chamber 20 into a suction part and a compression part. As shown in FIG. 2, the space capacity of the cylinder chamber 20 is maximized in a state where the blade 25 is most advanced into the cylinder chamber 20 and only the head of the fixing screw 24 is positioned in the escape space 31. And when it rotates 180 degrees from the position of FIG. 2, the space capacity of the cylinder chamber 20 becomes the minimum.

  When the compression mechanism 6 acts, the refrigerant gas is sucked into the cylinder chamber 20 via the refrigerant pipe P and is filled. Along with the eccentric revolving motion of the roller 23, the rolling contact position of the roller 23 with respect to the circumferential surface of the cylinder chamber 20 moves, and the volume of the compression portion formed in the cylinder chamber 20 is reduced. That is, the gas already introduced into the cylinder chamber 20 is gradually compressed.

  The rotary shaft 8 is continuously rotated, the capacity of the compression section partitioned and formed in the cylinder chamber 20 is further reduced, the gas is compressed, and the discharge valve is opened when the pressure rises to a predetermined pressure. The high-pressure gas is discharged and filled into the sealed case 5 through the upper and lower valve covers 15 and 18, and is further led out of the sealed case 5 from the refrigerant pipe P connected to the upper end of the sealed case 5.

The high-pressure gas discharged to the refrigerant pipe P is condensed and liquefied by the condenser 1, adiabatically expanded by the expansion device 2, evaporated by the evaporator 3, takes latent heat of evaporation from the surrounding air, and performs a refrigeration action. The refrigerant evaporated in the evaporator 3 is gas-liquid separated by the gas-liquid separator, and is again sucked into the compression mechanism 6 in the compressor S and circulates in the above-described path.
Since the compressor S has a configuration in which the roller 23 and the blade 25 are substantially integrated, the roller S and the blade 25 are separated from each other in comparison with a general compressor in which the roller and the blade are separately formed. There is a merit such as reduction of friction loss and leakage between the two. On the other hand, the distance L from the center of the roller 23 to the front end surface of the blade 25 becomes longer, and the inclination angle of the component parts at the time of assembly is restricted, and the accuracy of parts such as squareness is required more strictly.

  In the above-described embodiment, the ball bearing 22 is interposed between the roller 23 and the crank portion 8 a provided on the rotating shaft 8. Since the ball bearing 22 has a degree of freedom such as inclination, the allowable inclination angle of the roller 23 can be increased. Of course, since the ball bearing 22 also has an allowable inclination angle, there is a limit in use.

FIG. 11 shows the ratio (L / R) between the distance L from the center of the roller to the tip of the blade and the outer radius R of the roller in a rolling piston type compressor in which the roller and the blade are integrated, and the defect rate (depending on one piece). It is a characteristic figure which shows the relationship of wear rate.
A broken line curve is a case where there is no ball bearing between the crank portion and the roller, and a solid line curve is a case where the ball bearing is interposed between the crank portion and the roller. From this figure, when there is no ball bearing between the roller 23 and the rotating shaft crank portion 8a, if L / R exceeds 1.5, the one-piece contact due to the inclination of the component in which the roller 23 and the blade 25 are integrated. It can be seen that the defect rate suddenly occurs.

  On the other hand, in the case where the roller 23 and the blade 25 are integrated, and the ball bearing 22 is interposed between the rotating shaft crank portion 8a and the roller 23, L / R is about 1.5. Then, the defect rate due to one piece does not occur. However, when L / R exceeds 2, a defective rate due to one piece occurs.

  Therefore, as in the present embodiment, the distance L from the center of the roller 23 to the tip surface of the blade 25 is limited to twice or less (L <2R) of the outer peripheral radius R of the roller 23. Therefore, in the rolling piston type compressor in which the roller 23 and the blade 25 are integrally formed, it is possible to prevent performance degradation and part hitting of the parts, increase the margin of parts accuracy and assembly accuracy, and improve productivity. can get.

  In the above-described structure, the oil grooves 35 and 36 are provided on the thrust surfaces of the blade 25 and the roller 23, and the oil groove 35 of the blade 25 and the oil groove of the roller 23 are combined in an integrated manner. 36 communicate with each other. In addition, the main bearing 14 and the valve cover 15 are provided with an oil escape passage 37 communicating with the escape space 31.

That is, in the rolling piston compressor S, there are a plurality of locations where gas leakage occurs during the compression operation. Among them, gas leakage from the thrust surface of the blade 25 is likely to occur because it is difficult to supply lubricating oil to the thrust surface portion.
Therefore, in a structure in which the roller 23 and the blade 25 are manufactured as separate parts and integrally joined by assembly, the oil grooves 35 and 36 are provided along the thrust surfaces of the blade 25 and the roller 23, and the thrust surface of the blade 25 is provided. Refueling is possible.

Thus, the lubricating oil sucked up from the oil reservoir 9 by the oil pump provided at the lower end of the rotary shaft 8 can be reliably and sufficiently supplied to the thrust surface of the blade 25 via the inner peripheral portion of the roller 23. , Gas leakage can be prevented and sealing performance can be improved.
Thereafter, the lubricating oil is guided to the escape space 31 to be filled, and is guided to the sealed case 5 from here through the oil escape passage 37 and finally returns to the oil reservoir 9. In particular, since the oil escape passage 37 is provided only on the upper side of the escape space portion 31, the lubricating oil is guided to the oil escape passage 37 after filling the escape space portion 31. Thereby, it is possible to prevent the gas from leaking through the gap with the blade 25 or the bush 33, and more reliably prevent the compression performance from being lowered.

  In the compressor S having the above-described structure, a processing escape portion is not provided at a connecting portion between the outer peripheral portion of the roller 23 and the attachment portion of the blade 25. By eliminating the escape portion, the residual gas in the cylinder chamber 20 can be reduced and the compression performance can be prevented from being lowered.

  That is, when processing the roller and the blade as an integral part, it is difficult to process the connecting portion between the outer peripheral portion of the roller and the connecting portion of the blade, and therefore it is necessary to provide a clearance for processing. However, the ratio of the residual gas at the time when the gas compressed to a predetermined pressure is completely discharged from the cylinder chamber increases, and the compression performance deteriorates due to re-expansion.

In the above-described configuration in which the roller 23 and the blade 25 are manufactured as separate parts and the roller 23 and the blade 25 are integrated via the fixing screw 24, the roller 23 and the blade 25 are processed at the connecting portion between the outer peripheral portion of the roller 23 and the straight portion of the blade 25. There is no escape part, and the reduction of residual gas and compression performance are prevented.
In the above embodiment, the base end surface of the blade 25 is formed into a curved surface having the same radius of curvature as the roller 23, and the base end surface of the blade 25 is in close contact with the outer peripheral surface of the roller 23. It is not limited to such a connection structure.

FIG. 6 is a plan view in which the connection structure between the blade 25A and the roller 23A is different according to the second embodiment. (The same components and the same parts as those in the first embodiment are given the same reference numerals and a new description is omitted. The same applies hereinafter.)
A concave portion 40 is provided in the outer peripheral portion of the roller 23A, and the concave portion 40 is set to have a dimensional shape that can be fitted with the base end portion j of the blade 25A. The base end j of the blade 25A has a planar shape perpendicular to the height direction and the longitudinal direction, like the tip.

A mounting hole 26 is provided so as to penetrate along the longitudinal direction from the distal end surface to the proximal end surface of the blade 25A, and a screw hole 27 is provided along the radial direction between the outer peripheral surface and the inner peripheral surface of the roller 23A.
When the fixing screw 24 is screwed into the screw hole 27 from the mounting hole 26 with the base end j of the blade 25A inserted into and abutted into the recess 40, the roller 23A and the blade 25A are configured as an integral part. .

  That is, in a general structure in which the roller and the blade are configured as separate parts, the blade end slides with respect to the peripheral surface of the roller, and leakage, friction loss, wear, and the like during this time become problems. Therefore, there are rollers and blades as one part from the beginning. However, since a part of the outer periphery of the roller is not circular, it is difficult to ensure the roundness of the outer periphery of the roller.

  Further, when the roller and the blade are integrally formed, the distance from the roller to the blade tip becomes longer. If the perpendicularity between the inner circumference of the roller and the thrust surface of the blade cannot be obtained sufficiently, or if the shape accuracy of the crank part cannot be obtained, the inclination of the roller and blade integrated parts in the cylinder increases, and the thrust surface Leakage at the top increases, causing a single contact.

Therefore, a compressor having a structure in which the roller and the blade are formed as separate parts and then fixed and integrated, as in [Patent Document 1] and [Patent Document 2] described above, is provided. Became.
In the above-mentioned [Patent Document 1], a fitting groove is formed on the outer periphery of the roller and coupled to a fitting portion provided on the blade, thereby integrating the roller and the blade. In the above [Patent Document 2], the vanes and the roller are integrated by connecting the two parallel planes of the vane and the central axis of the cylindrical outer peripheral surface of the roller with a bolt.

  However, in the technique of [Patent Document 1], it is difficult to obtain part accuracy such as squareness in processing of the fitting groove provided on the outer periphery of the roller and the fitting convex portion of the blade, and the two are completely fixed by a slight difference in shape. Is hard to get. A fixing method by press-fitting or the like has also been proposed, but with this method, it is difficult to obtain the perpendicularity of the parts after assembly.

  In the technique of [Patent Document 2], a part of the outer periphery of the roller is greatly shaved for fixing the bolt of the blade, so that it is difficult to obtain component accuracy such as roundness of the outer periphery of the roller. In order to escape the inclination of the roller and blade integrated parts, the spherical support member and the spherical bush are used. However, it is difficult to match these spherical surfaces in a practical process, and there is a risk that an excessive force acts on the contrary.

  On the other hand, in the first embodiment and the second embodiment described above, since the rollers 23 and 23A and the blades 25 and 25A are fixed and integrated with the fixing screw 24, the rollers 23 and 23A are integrated. There is no processing to greatly cut the outer periphery of 23A. Since only hole drilling or tapping is performed, it is easy to ensure component accuracy such as the roundness of the rollers 23 and 23A and the parallelism of the blades 25 and 25A.

  Further, since the rollers 23 and 23A do not require escape portions, milling or the like is not required, and even when the rollers 23 and 23A are coupled to the blades 25 and 25A, the inner diameter of the rollers 23 and 23A and the slices of the blades 25 and 25A are sliced. A perpendicularity to the surface and a parallelism to the side surface can be secured.

  During operation of the compressor, the blades 25 and 25A partition the compression portion and the suction portion and receive differential pressure on the side surfaces, so it is necessary to take measures so as not to deviate from the fixed positions with the rollers 23 and 23A. As described above, it is possible to connect the mounting hole 26 and the screw hole 27 by a simple method, that is, additional processing, and maintain the coupling force against the force acting by the differential pressure during compressor operation.

  Compared with the conventional structure in which the roller and the blade are separated from each other, the processing method is not greatly changed. A structure in which a plurality of fixing screws 24 are attached at predetermined intervals in the height direction of the rollers 23, 23A or a plurality of fixing screws 24 in the thickness direction of the blades 25, 25A is effective for increasing strength retention. is there.

  In particular, as shown in FIG. 6, the width dimension B in the width direction, which is a direction orthogonal to the longitudinal direction of the blade 25A, is larger than twice the eccentric amount e of the rotating shaft crank portion 8a (B> 2e). It is set.

  That is, as means for improving the sealing performance of the compressor S, the oil supply conditions, the substantial length of the seal, the clearance, and the like are important. Therefore, the oil grooves 35 and 36 are provided on the slicing surfaces of the roller 23 and the blade 25, and the length of the seal portion that maintains an appropriate clearance while ensuring the oil supply efficiency is required.

  The maximum width at which the blade 25A swings is smaller than twice the eccentric amount e of the crank portion 8a (= 2e). By setting B> 2e, which is the above requirement, there is a place where the thrust surface of the blade 25A is always in contact with the thrust surface of the main bearing 14 or the sub-bearing 17 that becomes the mating contact surface. And, by the structure in which the lubricating oil supplied through the oil grooves 35 and 36 is present at the above location, it is possible to ensure the sealing performance with respect to the high-pressure side compression portion and the low-pressure side suction portion across the blade 25A.

  Note that this condition can also be applied to a structure in which the base end surface of the blade 25 is a curved surface having the same curvature radius as the outer peripheral surface of the roller 23 as shown in FIG. 2 (first embodiment). It is.

FIG. 7 is a partial cross-sectional plan view of a compression mechanism 6A having a further different configuration as the third embodiment. (The ball bearing 22 is omitted here.)
The blade 25B is formed by integrally connecting a parallel part m and a circular part n, and a cross section is formed in a so-called keyhole shape (although it is solid). The cylinder 13 is provided with a circular hole 30A, and the circular part n of the blade 25B is fitted in a swingable manner. The parallel part m of the blade 25B protrudes into the cylinder chamber 20, and is slidably fitted into a recess q provided on the outer periphery of the roller 23B.

  As the rotating shaft 8 rotates, the roller 23B performs eccentric revolving motion in the cylinder chamber 20, and the parallel portion m of the blade 25B reciprocates in the recess q provided in the roller 23B. The parallel part m of the blade 25B divides the inside of the cylinder chamber 20 into a compression part and a suction part, which is the same as described above, and the compression operation is performed smoothly.

  In such a structure, the pair of bushes 33 as described above with reference to FIG. 2 is not necessary, and the cost of parts can be reduced. Then, by providing an oil hole or oil groove 45 between the recess q provided in the roller 23B and the crank portion 8a, the lubricating oil is guided from the inner periphery of the roller 23B, and the sealing property between the roller 23B and the blade 25B is improved. Can be increased.

  In the above-described embodiment, a rolling piston type compressor has been described. However, the present invention is not limited to this, and can naturally be applied to an expander and other fluid machines. In the implementation stage, the constituent elements can be modified and embodied without departing from the spirit of the invention, and various inventions can be formed by appropriately combining a plurality of constituent elements disclosed in the above-described embodiments.

The partial longitudinal cross-sectional view and refrigeration cycle block diagram of the rolling piston type compressor which concern on 1st Embodiment in this invention. The top view of the compression mechanism part based on the embodiment. The top view of a part of compression mechanism part based on the embodiment. Sectional drawing of a part of compression mechanism part based on the embodiment. Sectional drawing of a part of compression mechanism part based on the embodiment. The top view of a part of compression mechanism part based on 2nd Embodiment in this invention. The cross-sectional top view of a part of compression mechanism part based on 3rd Embodiment in this invention. Explanatory drawing regarding the clearance in the compression mechanism part in this invention. Explanatory drawing of the allowable inclination angle at the time of making a roller and a blade into a separate structure. Explanatory drawing of the allowable inclination angle at the time of integrating a roller and a braid | blade. The characteristic view showing the relationship between the ratio of the distance L from the roller center to the blade tip radius and the roller outer radius R, and the defect rate when the roller and the blade are integrated and there is a case where there is no ball bearing.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 20 ... Cylinder chamber, 13 ... Cylinder, 8a ... Crank part, 8 ... Rotating shaft, 23 ... Roller, 25 ... Blade, 22 ... Ball bearing, 27 ... Screw hole, 26 ... Mounting hole, 24 ... Fixing screw, 40 ... Recess, 35 ... oil groove of blade (36), oil groove of 36 (roller), S ... rolling piston compressor, 1 ... condenser, 2 ... expansion device, 3 ... evaporator.

Claims (5)

A cylinder with a cylinder chamber;
A rotary shaft provided through the cylinder chamber of the cylinder and having a crank portion at a portion facing the cylinder chamber;
A roller that engages with the crank portion of the rotating shaft and makes an eccentric revolving motion in the cylinder chamber as the rotating shaft rotates;
A blade that is provided integrally with the roller, swings in accordance with the eccentric revolving motion of the roller, and partitions the cylinder chamber into a compression portion and a suction portion;
A ball bearing interposed between the crank portion of the rotating shaft and the roller;
A fluid machine characterized in that a distance L from the center of the roller to the tip surface of the blade is set to be not more than twice the outer peripheral radius R of the roller (L <2R).   The roller and the blade are formed separately, the roller is provided with a screw hole along a radial direction, and the blade is provided with a mounting hole along a longitudinal direction perpendicular to the height direction. 2. The fluid machine according to claim 1, wherein the blade is integrally attached and fixed to the roller by screwing a fixing screw into the screw hole through the use hole.   The roller is provided with a recess capable of being fitted with a blade end at an outer peripheral portion, and the roller end is inserted and abutted into the roller recess and fixed with the fixing screw. 2. The fluid machine according to 2.   An oil groove is provided along the longitudinal direction on the thrust surface of the blade, and an oil groove is provided along the radial direction on the thrust surface of the roller, and the oil groove is combined with the blade and the roller integrally. The fluid machine according to claim 1, wherein the fluid machines communicate with each other.   A refrigeration cycle apparatus comprising the compressor as a fluid machine according to any one of claims 1 to 4, a condenser, an expansion device, and an evaporator.

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