JP2008157101A - Rotary compressor and refrigerating cycle device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To maintain strength of a fore side of a blade, and to machine a blade and a blade groove without needing high machining accuracy. <P>SOLUTION: A rotary compressor comprises: a blade fitting groove 23 provided in a cylinder 8A; and a blade 15a reciprocatively provided in the blade fitting groove 23, in which a tip is abutted on a circumferential face of a roller 13a by receiving pressure of high pressure gas at its bearing face at a rear end, and the inside of the cylinder chamber 14a is partitioned into a suction chamber 14a<SB>1</SB>and a compression chamber 14a<SB>2</SB>along a rotation direction of the roller 13a. The thickness of a rear side of the blade 15a is smaller than that of the fore side, and a spacer 31 is inserted in a clearance 30 formed between the rear side of the blade with a small thickness and an inner wall face of the blade fitting groove 23. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to, for example, a rotary compressor incorporated in a refrigeration cycle apparatus such as a heat pump hot water supply apparatus, and a refrigeration cycle apparatus.

  In this type of rotary compressor, an electric motor unit and a compression mechanism unit driven by the electric motor unit are housed in a sealed case, and gas compressed by the compression mechanism unit is once discharged into the sealed case. Yes.

  The compression mechanism unit houses a roller in a cylinder chamber of the cylinder so as to be eccentrically rotatable. The cylinder is provided with a blade fitting groove, and the blade is accommodated in the blade fitting groove so as to be reciprocally movable. The back side of the blade is pressed by the action of high-pressure gas guided from a pressing member or a compression mechanism, and the tip is in contact with the peripheral surface of the roller and slides. The blade chamber partitions the cylinder chamber into a suction chamber and a compression chamber along the rotation direction of the roller. A suction pipe is connected to the suction chamber, and a discharge part of the compression chamber is opened in the sealed case.

  By the way, in order to partition the cylinder chamber into the suction chamber and the compression chamber by the blade, a predetermined pressing force is necessary. However, if the pressing force is too large, the sliding loss increases and the performance is deteriorated. In particular, when carbon dioxide is used as the refrigerant, the pressure difference between the front and back sides of the blade is large, and excessive wear may occur on the blade and the roller.

Therefore, it is considered that the pressing force of the blade is appropriately adjusted by reducing the pressure receiving area on the back side of the blade (see, for example, Patent Document 1).
JP-A-4-178989

  However, the above-described prior art has a problem that since the blade is thinned as a whole, the strength on the tip end side of the blade is lowered, and deformation is easily caused when sliding with the roller.

  Moreover, in order to form a thin blade as a whole, there is a problem that high processing accuracy is required and it is difficult to process the blade.

  Furthermore, there is a problem that the blade fitting groove has to be processed narrowly in response to the thinning of the blade, so that high processing accuracy is required and it is difficult to process the blade fitting groove.

  The present invention has been made paying attention to the above circumstances, and its object is to reduce the strength of the blade tip and the blade fitting without reducing the strength on the tip side of the blade and without requiring high processing accuracy. It is an object of the present invention to provide a rotary compressor and a refrigeration cycle apparatus that can process a joint groove.

  In order to solve the above-described problem, the first aspect of the present invention includes a motor case and a rotary compression mechanism connected to the motor in a sealed case, and the compression mechanism is stored in a cylinder chamber of the cylinder. In a rotary compressor that has a roller that is eccentrically rotated by the electric motor unit and that is compressed and discharged by the eccentric rotation of the roller, the rotary fitting that temporarily discharges the compressed gas into the hermetic case includes a blade fitting provided in the cylinder. A reciprocating motion is provided in the joint groove and in the blade fitting groove, and the pressure of the high-pressure gas in the sealed case is received by the pressure-receiving surface at the rear end so that the tip is brought into contact with the peripheral surface of the roller. A blade that divides the cylinder chamber into a suction chamber and a compression chamber along the rotation direction of the roller, and the thickness of the rear side of the blade is smaller than the thickness of the tip side. The wall thickness dimension in a gap formed between the rear side and the inner wall surface of the blade fitting groove of the blade to be small to insert the spacer.

  Further, according to the fifth aspect of the present invention, a radiator, an expansion device, and an evaporator are sequentially connected to the rotary compressor according to the first aspect via a refrigerant pipe to constitute a refrigeration cycle.

  ADVANTAGE OF THE INVENTION According to this invention, while the deformation | transformation of the front-end | tip part side of a braid | blade can be prevented, favorable compression is attained, and a braid | blade and a braid | blade fitting groove | channel can be processed without requiring a high processing precision.

Hereinafter, the present invention will be described in detail with reference to embodiments shown in the drawings.
FIG. 1 shows a refrigeration cycle apparatus according to an embodiment of the present invention.
The refrigeration cycle apparatus includes a vertical rotary compressor 1. The rotary compressor 1 includes a sealed case 1a. A compression mechanism unit 2 is provided on the lower side of the sealed case 1a, and an electric motor unit 3 is provided on the upper side. The electric motor unit 3 and the compression mechanism unit 2 are connected via a rotating shaft 4.

  The electric motor unit 3 includes a stator 5 fixed to the inner surface of the sealed case 1a, and a rotor 6 that is provided inside the stator 5 with a predetermined gap and into which the rotating shaft 4 is inserted. The compression mechanism unit 2 includes two cylinders 8A and 8B that are arranged up and down with a partition plate 7 interposed therebetween.

  A main bearing 9 is overlaid on the upper surface of the upper cylinder 8A, and is attached to the cylinder 8A via a mounting bolt 10 together with a valve cover a. A sub-bearing 11 is superimposed on the lower surface portion of the lower cylinder 8B, and is attached to the upper cylinder 8A via a mounting bolt 12 together with the valve cover b.

  On the other hand, the lower side of the rotating shaft 4 is rotatably supported by a main bearing 9 and a sub bearing 11. Two eccentric portions 4a and 4b are integrally formed on the lower side of the rotating shaft 4 with a phase difference of about 180 °. The eccentric parts 4a and 4b are located in the cylinders 8A and 8B, and rollers 13a and 13b are fitted on the peripheral surfaces thereof.

  The cylinders 8A and 8B are divided into upper and lower surfaces by the partition plate 7, the main bearing 9 and the auxiliary bearing 11, and cylinder chambers 14a and 14b are formed therein. Rollers 13a and 13b are accommodated in the cylinder chambers 14a and 14b so as to be rotatable eccentrically.

  The cylinders 8A and 8B are provided with blades 15a and 15b that partition the cylinder chambers 14a and 14b into a high pressure side and a low pressure side. The blades 15a and 15b are pressed toward the eccentric rollers 13a and 13b by the spring members 26a and 26b.

  Suction pipes 16a and 16b are connected to the cylinders 8A and 8B, and one end sides of the cylinders 8A and 8B are joined outside the sealed case 1a and connected to the accumulator 17.

  On the other hand, a lead-out pipe 18 is connected to the upper end of the sealed case 1a. This lead-out pipe 18 is connected to the accumulator 17 via the radiator 19, the expansion mechanism 20, and the evaporator 21, and, for example, a refrigeration cycle such as a heat pump hot water supply device is configured. A water circuit 22 is connected to the radiator 19.

  FIG. 2 is a plan view showing the upper and lower cylinders 8A and 8B.

  Since the upper and lower cylinders 8A and 8B are configured in substantially the same manner, the upper cylinder 8A will be described as a representative (in the following embodiments, the upper cylinder 8A will also be described as a representative).

  The upper cylinder (hereinafter referred to as a cylinder) 8A is provided with an opening for forming a cylinder chamber 14a. The cylinder 8A is provided with a blade fitting groove 23 from the cylinder chamber 14a toward the outer diameter side. A blade 15a is fitted in the blade fitting groove 23 so as to be capable of reciprocating.

  The blade 15a has a large thickness on the front end side in sliding contact with the roller 13a and a small thickness on the rear side. That is, the thickness of the rear side of the blade 15a is approximately ½ of the thickness of the tip side. The thickness of the blade 15 a on the tip side is substantially equal to the groove width of the blade fitting groove 23. A gap 30 is formed between the rear side where the thickness of the blade 15 a is small and the inner wall surface of the blade fitting groove 23.

  A spacer 31 is provided in a portion of the blade fitting groove 23 on the side opposite to the cylinder chamber. The spacer 31 constitutes a closed space portion 32 by inserting the tip end side into the gap 30. A protrusion 31 a is formed integrally with the spacer 31, and the protrusion 31 a faces the end 23 a of the blade fitting groove 23.

In addition, two springs 26a _{1 and} 26a ₂ are disposed on the side opposite to the cylinder chamber of the blade fitting groove 23, and the rear end surface (pressure receiving surface) of the blade 15a is pressed by _one spring 26a ₁ , and the other spring 26a ₁ is pressed. spacer 31 is pressed by the spring 26a _2.

Blade 15a is adapted to abut against the peripheral surface of the roller 13a of the front end portion by the pressing of the spring 26a ₁ partitions the cylinder chamber 14a to the suction chamber 14a ₁ and the compression chamber 14a _2. The spacer 31 is held with the protrusion 31 a abutting against the end 23 a of the blade fitting groove 23 by pressing of the spring 26 a ₂ .

  The non-cylinder chamber side of the blade fitting groove 23 is opened in the sealed case 1a, and has the same high pressure as the pressure of the high-pressure gas discharged into the sealed case 1a. The blade 15a is pressed by a pressure difference between the inside and outside of the cylinder, and its tip is brought into contact with the peripheral wall surface of the roller 13a.

The pressing force of the blade 15a by the casing pressure is also several tens of times of the pressing force of the spring 26a ₁ provided in the cylinder 8A, originally, the biasing force of the spring 26a ₁ except at startup, that particularly require There is no.

  The blade 15a reciprocates along the blade fitting groove 23a based on the eccentric rotation of the roller 13a along the inner peripheral wall of the cylinder chamber 14a.

  In the configuration described above, when an operation signal is transmitted to the motor unit 3, the rotary shaft 4 is driven to rotate, and the rollers 13a and 13b provided in the upper and lower cylinders 8A and 8B rotate eccentrically in the cylinder chambers 14a and 14b. Do.

  The space capacity of the cylinder chambers 14a, 14b is maximized in a state where the positions where the rollers 13a, 13b are in rolling contact with the inner peripheral surface of the cylinder chamber 14 and the positions where the blades 15a, 15b are in contact with the rollers 13a, 13b substantially coincide. Become. At this time, the refrigerant gas is sucked into the cylinder chambers 14a and 14b of the upper and lower cylinders 8A and 8B from the accumulator 17 through the suction pipes 16a and 16b and is filled.

As the rollers 13a and 13b rotate eccentrically, the rolling contact positions of the rollers 13a and 13b with respect to the inner peripheral surfaces of the cylinder chambers 14a and 14b move, and the volumes of the compression chambers 14a ₂ and 14b ₂ gradually decrease. As a result, the refrigerant gas previously introduced into the cylinder chambers 14a and 14b is gradually compressed.

When the rotary shaft 4 is continuously rotated, the volumes of the compression chambers 14a ₂ and 14b ₂ are further reduced and the refrigerant gas is compressed. When the pressure rises to a predetermined pressure, a discharge valve (not shown) is opened, and the valve covers a and b are interposed. Thus, the high-pressure refrigerant gas is discharged into the sealed case 1a. When a predetermined time elapses after the high-pressure refrigerant gas is discharged in this way, the amount of the high-pressure gas discharged from the cylinder chambers 14a and 14b increases, and the inside of the sealed case 1a becomes a predetermined high pressure state.

  As a result, the high pressure of the discharge gas acts on the rear end surfaces of the blades 15a and 15b provided in the cylinders 8A and 8B, that is, the pressure receiving surfaces, and the tip portions are brought into contact with the peripheral wall surfaces of the rollers 13a and 13b with an appropriate pressing force. The compression operation as described above is continued. At this time, the spacer 31 also receives the pressure of the high-pressure discharge gas, and the protrusion 23 a is brought into contact with the end 23 a of the blade fitting groove 23 to be fixedly held.

  The high-pressure gas filled in the sealed case 1a is discharged from the outlet pipe 18 above the sealed case 1a. The derived high-pressure gas is guided to the radiator 19 to dissipate heat, adiabatically expands by the expansion mechanism 20, and the evaporator 21 takes away latent heat of evaporation from the heat exchange air. The evaporated refrigerant is guided to the accumulator 17, where it is separated into gas and liquid, and is again sucked into the compressor mechanism 2 of the compressor through the suction pipes 16a and 16b and circulates in the above-described path.

  As described above, according to this embodiment, the thickness of the rear side of the blades 15a and 15b is made smaller than the thickness of the tip side, and the rear end side of the blades 15a and 15b is fitted to the blade. Since the spacer 31 is inserted into the gap 30 formed between the inner wall surface of the joint groove 23, the area of the rear end surfaces of the blades 15a and 15b, that is, the pressure receiving surfaces can be reduced.

  Therefore, the force of the high-pressure gas received by the blades 15a and 15b can be reduced, and the tip portion can be pressed against the peripheral wall surface of the rollers 13a and 13b with an appropriate force, and the blade 15a and 15b can be pressed between the rollers 13a and 13b. The sliding loss can be reduced, the occurrence of wear can be prevented, and good compression performance can be maintained.

  Also, since the thickness of the blades 15a and 15b on the tip side is larger than the thickness on the rear side, the strength on the tip side can be maintained sufficiently, and deformation can be prevented and good compression can be achieved. Become.

  Further, since the groove width dimension of the blade fitting groove 23 is formed corresponding to the thickness dimension of the blades 15a and 15b on the tip side, the blade fitting groove 23 is easily processed.

  Furthermore, since the thickness of the blades 15a and 15b is also reduced only on the rear side, the processing becomes easier as compared with the case where the thickness is reduced as a whole.

  FIG. 3 shows a cylinder structure according to the second embodiment of the present invention.

  Note that the same parts as those shown in the first embodiment described above are denoted by the same reference numerals and detailed description thereof is omitted (the same is omitted in each embodiment described later).

In the second embodiment, and communicated the closed space 32 formed by the blade 15a and the spacer 31 to the blade fitting groove 23 to the suction chamber 14a ₁ of the cylinder chamber 14a. That is, the communication path 41 is formed in the cylinder 8 </ b> A, and the closed space portion 32 and the suction chamber 14 a ₁ of the cylinder chamber 14 communicate with each other through the communication path 41.

  According to the second embodiment, the gas is compressed in the closed space 32 based on the movement of the blade 15a toward the non-cylinder side by the rotation of the roller 13a. To the suction chamber 14a side. Therefore, there is an advantage that it is possible to prevent the pressing force of the tip of the blade 15a against the peripheral wall surface of the roller 13a from becoming excessive. The communication path 41 may be formed in the partition plate 7, the main bearing 9, or the sub bearing 11.

  FIG. 4 shows a cylinder structure according to a third embodiment of the present invention.

In the second embodiment described above, but communicated with a suction chamber 14a ₁ of the closed space portion 32 and the cylinder chamber 14a through the communication passage 41 formed in the cylinder 8A, in the third embodiment, the wall thickness of the blade 15a forming the communication passage 51 to the front end portion of the large, thereby communicating the suction chamber 14a ₁ of the closed space portion 32 and the cylinder chamber 14a through the communicating passage 51.

  This third embodiment also has an advantage that it is possible to prevent the pressing force of the tip of the blade 15a against the peripheral wall surface of the roller 13a from being excessive as in the second embodiment.

  FIG. 5 shows a cylinder structure according to a fourth embodiment of the present invention.

In the first embodiment described above, the spacer 31 is inserted into the gap 30 formed between the one side surface on the rear side and the inner wall surface of the blade fitting groove 23 where the thickness of the blade 15a is small. However, in the fourth embodiment, the gaps 61 and 62 formed between the both side surfaces on the rear side and the inner wall surface of the blade fitting groove 23 that reduce the wall thickness of the blade 15a are formed in the gaps 61 and 62, respectively. Spacers 63 and 64 are inserted, respectively. The spacers 63 and 64 have their projections 63a and 64a joined to the step portions 23a ₁ and 23a ₂ of the blade fitting groove 23, respectively.

  This fifth embodiment also provides the same operations and effects as the first embodiment described above.

  In addition, according to above-mentioned embodiment, although the 2 cylinder type compressor provided with two cylinder chambers was demonstrated, it is not limited to this, A 1 cylinder type rotary compressor, 3 cylinders or more It can be applied to a multi-cylinder rotary compressor.

  Further, the present invention is not limited to the above-described embodiment as it is, and can be embodied by modifying the constituent elements without departing from the scope of the invention in the implementation stage. Furthermore, various inventions can be formed by appropriately combining a plurality of constituent elements disclosed in the above-described embodiments. For example, you may delete some components from all the components shown by embodiment mentioned above. Furthermore, you may combine the component covering different embodiment suitably.

The figure which shows the refrigerating-cycle apparatus provided with the rotary type | formula hermetic compressor which is the 1st Embodiment of this invention. The figure which shows the cylinder structure of the rotary compressor of FIG. The figure which shows the cylinder structure which is the 2nd Embodiment of this invention. The figure which shows the cylinder structure which is the 3rd Embodiment of this invention. The figure which shows the cylinder structure which is the 4th Embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Sealing case, 2 ... Compression mechanism part, 3 ... Electric motor part, 8A ... Upper cylinder, 8B ... Lower cylinder, 13a, 13b ... Roller, 14a ₁ ... Suction chamber, 14a ₂ ... Compression chamber, 15a, 15b ... Blade, DESCRIPTION OF SYMBOLS 19 ... Radiator, 20 ... Expansion device, 21 ... Evaporator, 23 ... Blade fitting groove, 30 ... Gap, 31 ... Spacer, 32 ... Closed space part, 41, 51 ... Communication path.

Claims (3)

An electric motor part and a rotary compression mechanism part connected to the electric motor part are housed in a sealed case, and the compression mechanism part includes a roller that is eccentrically rotated by the electric motor part in a cylinder chamber of the cylinder, and the roller In the rotary type compressor that once discharges the compressed gas compressed and discharged by the eccentric rotation of
A blade fitting groove provided in the cylinder;
It is provided in the blade fitting groove so as to be able to reciprocate, and by receiving the pressure of the high-pressure gas in the sealed case at the pressure-receiving surface at the rear end, the tip end portion is brought into contact with the peripheral surface of the roller, and the inside of the cylinder chamber is A blade that partitions the suction chamber and the compression chamber along the rotation direction of the roller,
The thickness on the rear side of the blade is smaller than the thickness on the tip side,
A rotary compressor characterized in that a spacer is inserted into a gap formed between a rear side of a blade having a small thickness and an inner wall surface of the blade fitting groove.   2. The rotary compressor according to claim 1, wherein a closed space formed by the blade and the spacer is communicated with the suction chamber of the cylinder through the communication path.   A refrigeration cycle apparatus comprising: a rotary compressor according to claim 1, wherein a radiator, an expansion device, and an evaporator are sequentially connected via a refrigerant pipe to constitute a refrigeration cycle.

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