JP5971048B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor including a compression mechanism that compresses a working fluid between a rotor and a cylinder by a blade that protrudes and protrudes with respect to a spiral groove of the rotor.

  A conventionally known compressor disclosed in Patent Document 1 includes a cylinder, a roller that is eccentrically disposed in the cylinder and provided with a spiral groove, and a helical shape that is slidably fitted in the spiral groove. It is a fluid machine provided with the compression mechanism part which consists of a braid | blade. In a compressor of this type, the low pressure side of the blade is pressed against the low pressure side surface of the spiral groove due to the pressure difference between the low pressure side and the high pressure side. The life could be shortened. As a countermeasure against this problem, it has been proposed to form a solid lubricating film on the side surface of the spiral groove. In particular, the solid lubricant film on the low pressure side, which often slides compared to the high pressure side during operation, tends to wear more than the solid lubricant film on the high pressure side.

JP 2005-325827 A

  Therefore, in the compressor of Patent Document 1, by applying a solid lubricant to the low-pressure side wall and the high-pressure side wall of the spiral groove, and further covering the solid lubricant on the low-pressure side wall with a thick film, The sliding resistance between the blade and the rotor is suppressed, and the wear of the spiral groove surface is suppressed. However, although the solid resin film to be applied has an effect of reducing a certain sliding resistance, the applied solid resin film has a structure that easily wears, and wear progresses by repeated sliding, and the film thickness decreases. For this reason, in the compressor of patent document 1, it does not become a fundamental solution with respect to the leakage of the working fluid from a high pressure side to a low pressure side.

  Therefore, the present invention has been made in view of the above problems, and has a helical compression mechanism that compresses a working fluid between a rotor and a cylinder by a blade that protrudes and protrudes with respect to a spiral groove of the rotor. An object of the compressor is to suppress leakage of working fluid from the high pressure side to the low pressure side by the mechanical characteristics of the compression mechanism section.

The present invention employs the following technical means to achieve the above object. That is, the present invention includes a cylinder (20), a roller ( 21 ) eccentrically provided on the inner side of the cylinder, and having a spiral groove ( 22, 22A ) formed in a spiral shape on the outer peripheral surface, and a spiral groove. A compression mechanism portion (2) including a blade ( 24, 24A ) fitted in and out of the motor, and a motor portion (3) for rotating the roller, and the blade is spiraled between the cylinder and the roller by the blade. The compressor (1) compresses the working fluid in the compression chamber (23) formed in a shape,
The blade has a first divided portion ( 240 ) and a second divided portion ( 241 ) that are divided so that portions fitted into the spiral groove are aligned in the rotation axis direction of the roller,
The first dividing section, the distal end portion facing the bottom surface of the helical groove, the pressure of the intruding working fluid in a spiral groove first force the first division section in a direction away from the second splitting unit acts Having a pressure receiving surface ( 240a ),
In the second divided portion, a force acts on the tip portion facing the bottom surface ( 221 ) of the spiral groove in a direction away from the first divided portion by the pressure of the working fluid that has entered the spiral groove. 2 of the pressure receiving surface (241a) possess,
Each of the first pressure receiving surface and the second pressure receiving surface is formed by an inclined surface in which the side surface (222a, 222b) side of the spiral groove protrudes from the opposite side in the rotation axis direction.
The bottom surface of the spiral groove is formed in a shape along both the first pressure receiving surface and the second pressure receiving surface, and the first pressure receiving surface and the second pressure receiving surface are formed such that the blade is the most with respect to the spiral groove. It contacts the bottom surface of the spiral groove in a submerged state .

  In a compressor of a type in which a working fluid is compressed in a compression chamber formed by a blade between a cylinder and a roller, a high-pressure working fluid that has entered between the bottom surface of the spiral groove and the tip portion of the blade is compressed. Acts on the tip. According to the present invention, the high-pressure fluid acts on the first pressure receiving surface at the tip of the first divided portion and the second pressure receiving surface at the tip of the second divided portion. For this reason, the 1st division part is pushed in the direction away from the 2nd division part, is pressed against the side of the spiral groove located on the opposite side to the 2nd division part, and the 2nd division part is also kept away from the 1st division part. It is pushed in the direction and is pushed against the side surface of the spiral groove located on the opposite side to the first divided portion. In this manner, the first divided portion and the first divided portion that contact the high pressure side compression space on one side and the low pressure side compression space on the other side with the side surface of the spiral groove, respectively, across the blade in the rotation axis direction of the roller. It can be blocked by the two-divided part. For this reason, it is possible to construct a mechanism that prevents the high-pressure fluid from leaking into the compression space on the low-pressure side, so that it is possible to suppress a reduction in compression efficiency. Therefore, according to the present invention, the leakage of the working fluid from the high-pressure side to the low-pressure side can be suppressed by the constant mechanical feature of the compression mechanism portion that is not affected by the conventional wear progress.

  The reference numerals in parentheses of the above means are examples showing the correspondence with the specific means described in the embodiments described later, and do not limit the scope of the present invention.

It is a schematic sectional drawing which shows the outline | summary of the compressor of 1st Embodiment. It is a fragmentary perspective view which shows the braid | blade which concerns on 1st Embodiment. It is the figure which looked at the low voltage | pressure side edge part of the braid | blade which concerns on 1st Embodiment from the bottom face side of the helical groove | channel. It is the figure which looked at the high voltage | pressure side part of the braid | blade which concerns on 1st Embodiment from the bottom face side of the spiral groove. In FIG. 1, it is sectional drawing for demonstrating the relationship between the cross section of the braid | blade in the highest position, and a helical groove | channel. In FIG. 1, it is sectional drawing for demonstrating in detail the relationship between the cross section of the braid | blade in the lowest position, and a helical groove | channel. It is sectional drawing for demonstrating the relationship between the cross section of the braid | blade in the highest position, and a helical groove | channel about the compressor of 2nd Embodiment. It is sectional drawing for demonstrating the relationship between the cross section of the braid | blade in the highest position, and a helical groove | channel about the compressor of 3rd Embodiment. It is sectional drawing for demonstrating the relationship between the cross section of the braid | blade in the highest position, and a helical groove | channel about the compressor of 4th Embodiment. It is sectional drawing for demonstrating the relationship between the cross section of the braid | blade in the highest position, and a helical groove | channel about the compressor of 5th Embodiment.

  A plurality of modes for carrying out the present invention will be described below with reference to the drawings. In each embodiment, parts corresponding to the matters described in the preceding embodiment may be denoted by the same reference numerals, and redundant description may be omitted. When only a part of the configuration is described in each mode, the other modes described above can be applied to the other parts of the configuration. Not only combinations of parts that clearly show that combinations are possible in each embodiment, but also combinations of the embodiments even if they are not specified, unless there is a particular problem with the combination. Is also possible.

(First embodiment)
1st Embodiment which is one Embodiment of this invention is described using FIGS. In each of the cross-sectional views of FIGS. 5 and 6, the portion of the blade 24 is not shown with hatching in order to make the drawing easier to see. 1st Embodiment is an example of the compressor which concerns on this invention which has a helical compression chamber between a cylinder and a roller. The compressor which concerns on this invention can be used for a vehicle air conditioner, for example. In this case, the compressor constitutes a refrigeration cycle together with a condenser, a decompressor, an evaporator, and the like.

  As shown in FIG. 1, the compressor 1 includes at least a compression mechanism unit 2 and a motor unit 3. The motor unit 3 is a drive unit that drives the compression mechanism unit 2 and includes a motor stator and a motor rotor. The crankshaft 4 connects the motor unit 3 and the compression mechanism unit 2, and transmits the power of the motor unit 3 to the compression mechanism unit 2.

  The compression mechanism unit 2 includes a cylinder 20 that constitutes a part of the outer shape of the compression mechanism unit 2, a roller 21 that is eccentrically provided inside the cylinder 20 and that can be pivoted, and a space between the cylinder 20 and the roller 21 in a spiral shape. And a blade 24 that forms a compression chamber 23 that extends. The cylinder 20 is a cylindrical container that constitutes a pressure container. The cylinder 20 is formed with a suction port 20a for taking the working fluid into the pressure vessel on one side near the motor unit 3, and the side wall member 25 provided on the other side and forming the pressure vessel with the cylinder 20 has a compression mechanism. A discharge port 25a for discharging the working fluid compressed by the portion 2 to the outside is formed.

  The roller 21 is a metal cylindrical member that turns as the crankshaft 4 rotates, and is made of, for example, an aluminum alloy. The roller 21 is arranged such that its rotating shaft 210 extends in the horizontal direction as shown in FIG. The rotating shaft 210 is eccentric with respect to the central axis 200 of the compressor 1 or the compression mechanism unit 2. Accordingly, the roller 21 is energized to the motor unit 3 and its power is transmitted to the compression mechanism unit 2, whereby the roller 21 is driven to rotate eccentrically in the cylinder 20. The roller 21 is provided with a spiral groove 22 having a predetermined width dimension extending spirally on the outer peripheral surface. The spiral groove 22 is formed such that the pitch in the direction of the rotating shaft 210 gradually decreases from the left suction port 20a side in FIG. 1 toward the right discharge port 25a side in FIG.

  The blade 24 is a belt-like member that protrudes inward in the radial direction from the inner peripheral surface of the cylinder 20 and extends spirally along the spiral groove 22. The blade 24 is supported by the inner peripheral surface of the cylinder 20 and is formed so as to be able to appear and retract in the spiral groove 22. The blade 24 is formed in a shape and size that can freely enter and exit from the spiral groove 22. The blade 24 is an elastic member that can be deformed by an external force, and can be formed of a fluorocarbon resin such as polytetrafluoroethylene (PTFE).

  The blade 24 is fitted into the spiral groove 22 to partition the compression chamber 23 into a plurality of working chambers. The state blade 24 fitted in the spiral groove 22 has a pitch from the left suction port 20a side in FIG. 1 in the axial direction (for example, the direction of the rotating shaft 210) from the right discharge port 25a side in FIG. It is formed to be shorter toward the high pressure side. The pitch is an axial length corresponding to an interval between two adjacent blades 24 when viewed from a direction orthogonal to the axial direction. That is, the pitch is the axial length in the working chamber. For this reason, among the plurality of working chambers partitioned by the blade 24, the working chamber on the axial low pressure side has a smaller volume than the working chamber located on the axial high pressure side.

  As shown in FIGS. 2 to 4, the blade 24 includes a first divided portion 240 and a second divided portion 241 that are divided so that tip portions fitted in the spiral grooves 22 are aligned in the direction of the rotation shaft 210. Prepare. The first divided portion 240 and the second divided portion 241 are portions that bisect the entire longitudinal section of the blade 24, not just the tip portion of the blade 24 facing the bottom surface 221 of the spiral groove. The first divided portion 240 and the second divided portion 241 are not formed on the low pressure side end portion 24a of the blade 24, but are formed on the entire high pressure side portion 24b positioned on the high pressure side with respect to the low pressure side end portion 24a. . That is, the blade 24 has a shape in which only the low-pressure side end 24a is not divided into two forks. For example, the blade 24 is bifurcated in the other portion (the high-pressure side 24b) except for one end (the low-pressure side end 24a). It is in the form of disposable chopsticks.

  1, 5, and 6, the suction port 20 a is formed on the left side, and the discharge port 25 a is formed on the right side. Therefore, in the compression chamber 23, the blade 24 is sandwiched between the working chambers on the left side of the drawing. The right working chamber is at a higher pressure.

  As shown in FIGS. 5 and 6, the first dividing portion 240 includes a first pressure receiving surface 240 a that is inclined with respect to the rotation shaft 210 at a tip portion facing the bottom surface 221 of the spiral groove. The first pressure receiving surface 240a has a lower pressure side portion than a high pressure side portion so that the portion closer to the side surface 222a of the spiral groove has a larger protruding amount from the cylinder 20 than the portion closer to the second divided portion 241. Also forms a protruding slope. In other words, the vertical cross-sectional shape of the tip portion of the first divided portion 240 has a wedge shape in which the low-pressure side portion protrudes more than the high-pressure side portion.

  The second divided portion 241 includes a second pressure receiving surface 241 a that is inclined with respect to the rotating shaft 210 at a tip portion facing the bottom surface 221 of the spiral groove. The second pressure receiving surface 241a has a higher pressure side portion than a lower pressure side portion so that the portion close to the side surface 222b of the spiral groove has a larger protruding amount from the cylinder 20 than the portion close to the first divided portion 240. Also forms a protruding slope. In other words, the longitudinal cross-sectional shape of the tip portion of the second divided portion 241 has a wedge shape in which the high-pressure side portion protrudes from the low-pressure side portion. That is, the first pressure receiving surface 240a and the second pressure receiving surface 241a are formed on inclined surfaces in which the side surfaces 222a and 222b of the spiral groove protrude from the opposite side in the direction of the rotation shaft 210, respectively.

  In a state where a space is formed between the tip portion of the blade 24 and the bottom surface 221 of the spiral groove from the state shown in FIG. 6 where the blade 24 sinks most with respect to the roller 21, as shown in FIG. From the pressure PH of the working fluid that has entered the groove 22, the first pressure receiving surface 240a has a component force PHx in the direction of moving the first divided portion 240 away from the second divided portion 241 and the first divided portion 240 on the cylinder 20 side. The component force PHy in the direction of pushing is activated.

  Accordingly, the first dividing portion 240 located on the low pressure side is pushed to the low pressure side by the component force PHx, so that the low pressure side surface of the first dividing portion 240 is in close contact with the side surface 222a of the spiral groove located on the low pressure side. become. The second divided portion 241 located on the high pressure side is pushed to the high pressure side by the component force PHx, and the side surface on the high pressure side of the second divided portion 241 is pushed to the side surface 222b of the spiral groove located on the high pressure side. It becomes like this. Such a configuration is similarly ensured from the end of winding of the blade 24 to the end of winding, and each working chamber is reliably sealed. Even when the side surface of the second divided portion 241 and the side surface 222b of the spiral groove located on the high pressure side do not come into close contact with each other, the side surface of the first divided portion 240 and the side surface of the spiral groove on the low pressure side. Since 222a forms a seal structure, the low pressure side working chamber and the high pressure side working chamber can be shut off with the blade 24 interposed therebetween.

  Further, the bottom surface 221 of the spiral groove is formed in a shape along both the first pressure receiving surface 240a and the second pressure receiving surface 241a. That is, among the bottom surface 221 of the spiral groove, the low-pressure side bottom surface 221a formed on the low-pressure side is such that the portion on the side surface 222a side of the spiral groove has a larger dent amount than the portion on the second divided portion 241 side. A slope is formed so that the amount of dent increases from the high-pressure side portion toward the low-pressure side portion. In other words, the low-pressure side bottom surface 221a is formed in an inclined surface in which the side surface 222a side of the spiral groove is recessed from the opposite central portion in the direction of the rotation shaft 210. In addition, among the bottom surface 221 of the spiral groove, the high-pressure side bottom surface 221b formed on the high-pressure side is such that the portion on the side surface 222b side of the spiral groove has a larger dent amount than the portion on the first divided portion 240 side. A slope is formed so that the amount of dent increases as it goes from the low pressure side portion to the high pressure side portion. In other words, the high-pressure side bottom surface 221b is formed in an inclined surface in which the side surface 222b side of the spiral groove is recessed from the opposite central portion in the direction of the rotating shaft 210.

  Therefore, in the state shown in FIG. 6 in which the blade 24 sinks most with respect to the roller 21, the first pressure-receiving surface 240a and the second pressure-receiving surface 241a are respectively a low-pressure side bottom surface 221a and a high-pressure side bottom surface 221b (with spiral grooves). It comes into contact with the bottom surface 221).

  Next, the operation of the compressor 1 will be described. When the motor unit 3 is energized, the motor unit 3 is started, a rotating magnetic field is generated in the motor stator, and the motor rotor is rotationally driven. The rotational force of the motor rotor is transmitted to the crank portion via the crankshaft 4 to rotate the roller 21 eccentrically. Due to the eccentric rotation of the roller 21, the roller 21 slides and revolves in contact with the inner peripheral surface of the cylinder 20. Due to the eccentric rotation of the roller 21, each working chamber formed by the blade 24 between the cylinder 20 and the roller 21 changes in volume so that the volume gradually decreases while moving spirally in the axial direction of the roller 21. In each working chamber, the working fluid sucked through the suction port 20a due to the volume change is sequentially compressed and increased in pressure, and discharged from the high-pressure side compression chamber to the outside from the discharge port 25a.

  As shown in FIG. 5, in the compression process of the working fluid, there is a pressure difference between the high pressure side and the low pressure side of the compression chamber, so that the blade 24 that appears and disappears in the spiral groove 22 has a first end portion. The high pressure working fluid acting on the pressure receiving surface 240a and the second pressure receiving surface 241a causes the first divided portion 240 and the second divided portion 241 to be elastically deformed and pressed against the side surfaces 222a and 222b of the spiral groove, A seal structure is formed. Therefore, in the compressor 1 having a helical structure (spiral) compression chamber, leakage of the working fluid from the high pressure side to the low pressure side of the compression chamber can be suppressed.

  The effect which the compressor 1 of 1st Embodiment brings is demonstrated. The blade 24 includes a first divided portion 240 and a second divided portion 241 that are divided so that portions fitted in the spiral grooves are aligned in the rotation axis direction of the roller 21. In the first dividing portion 240, a force acts on the tip portion facing the bottom surface 211 of the spiral groove in a direction to move the first dividing portion 240 away from the second dividing portion 241 by the pressure of the working fluid that has entered the spiral groove 22. A first pressure receiving surface 240a. In the second divided portion 241, a force acts on the tip portion facing the bottom surface 211 of the spiral groove in a direction to move the second divided portion 241 away from the first divided portion 240 by the pressure of the working fluid that has entered the spiral groove 22. And a second pressure receiving surface 241a.

  According to such a configuration, the high-pressure working fluid is applied to the first pressure receiving surface 240 a formed at the tip of the first divided portion 240 and the second pressure receiving surface 241 a formed at the tip of the second divided portion 241. Works. For this reason, the first divided portion 240 is pushed away from the second divided portion 241 and is pressed against the side surface 222a of the spiral groove located on the opposite side of the second divided portion 241. The second divided portion 241 is also the second divided portion 241. It is pushed in the direction away from the first divided portion 240 and is pressed against the side surface 222 b of the spiral groove located on the opposite side of the first divided portion 240. In this way, the high pressure side compression space and the low pressure side compression space with the blade 24 sandwiched in the direction of the rotation shaft 210 of the roller 21, the side surface of the spiral groove, the first divided portion 240 and the second divided portion 241, Can be blocked by the mechanistic features. Thereby, the reduction of the compression efficiency in the helical compression chamber 23 can be suppressed. As described above, the compressor 1 that suppresses the leakage of the working fluid from the high-pressure side to the low-pressure side is obtained by the constant mechanical characteristics of the compression mechanism unit 2 that is not affected by the progress of wear.

  Further, according to the compressor 1, the first pressure receiving surface 240 a and the second pressure receiving surface 241 a are each formed by inclined surfaces in which the side surfaces 222 a and 222 b of the spiral groove protrude from the opposite side in the direction of the rotating shaft 210. Has been. According to this configuration, it is possible to form the first pressure receiving surface 240a and the second pressure receiving surface 241a on which the pressure of the high-pressure fluid can be effectively applied, so that the space between the blade 24 and the side surface 222 of the spiral groove can be formed. Can be constructed efficiently.

  Further, according to the compressor 1, the bottom surface 221 of the spiral groove is formed in a shape along both the first pressure receiving surface 240a and the second pressure receiving surface 241a. The first pressure receiving surface 240 a and the second pressure receiving surface 241 a are in contact with the bottom surface 222 of the spiral groove in a state where the blade 24 is sunk most with respect to the spiral groove 22.

  According to such a configuration, it is difficult for a gap to be formed between the tip portion of the blade 24 and the bottom surface 221 of the spiral groove in the most depressed state. For this reason, the dead space where the fluid spreads in the spiral groove 22 can be prevented. Therefore, the amount of fluid entering the spiral groove 22 can be reduced, and a desired sealing function that can prevent leakage with less fluid can be exhibited.

  Moreover, according to the compressor 1, the 1st division part 240 and the 2nd division part 241 are not only the front-end | tip part of the blade 24 which opposes the bottom face 221 of a spiral groove, but the part which bisects the whole longitudinal cross-section of the blade 24. It is. According to this, the 1st division part 240 and the 2nd division part 241 are parts which divide the blade 24 in the shape of a split chopstick.

  As described above, according to the configuration in which the longitudinal section of the blade 24 is vertically cracked, a space in which a high-pressure fluid enters in the spiral groove 22 is easily formed. Further, even when the first divided portion 240 and the second divided portion 241 are partially adhered when the working fluid is highly viscous, the high pressure fluid is between the two because both are originally vertically cracked portions. Easy to see and easy to apply pressure to pull them apart.

(Second Embodiment)
In 2nd Embodiment, 22 A of spiral grooves which are another forms with respect to 1st Embodiment are demonstrated with reference to FIG. In FIG. 7, the constituent elements having the same reference numerals as those in the drawing referred to in the first embodiment are the same elements, and the operational effects thereof are also the same. Hereinafter, different forms, operations, effects, and the like from the first embodiment will be described. FIG. 7 shows the relationship between the first divided portion 240 and the second divided portion 241 of the blade 24 and the spiral groove 22A at the highest position.

  A solid lubricating film 223 is formed on the inner wall of the spiral groove 22A. The solid lubricant film 223 is formed at least on the side surface 222Aa of the spiral groove and the side surface 222Ab of the spiral groove on which the first divided portion 240 and the second divided portion 241 slide. Further, the solid lubricating film 223 may be provided also on the bottom surfaces 221Aa and 221Ab of the spiral grooves. The solid lubricant film 223 can be formed of, for example, boron fiber, carbon fiber, or the like.

  According to the second embodiment, the sliding resistance between the blade 24 and the spiral groove 22A can be reduced, and the first divided portion 240 and the second divided portion 241, the side surface 222Aa of the spiral groove and the spiral groove can be reduced. The degree of contact with the side surface 222Ab can be appropriately controlled and maintained, and a desired sealing function can be exhibited over a long period of time.

(Third embodiment)
In the third embodiment, a blade 24A, which is another form of the first embodiment, will be described with reference to FIG. In FIG. 8, the constituent elements having the same reference numerals as those in the drawing referred to in the first embodiment are the same elements, and the operational effects thereof are also the same. Hereinafter, different forms, operations, effects, and the like from the first embodiment will be described. FIG. 8 shows the relationship between the first and second divided portions 240A and 241A of the blade 24A and the spiral groove 22 at the highest position.

  A solid lubricant film 242 is formed on the surface of the first divided portion 240A. The solid lubricating coating 242 is formed on at least the sliding surfaces of the first divided portion 240A and the second divided portion 241A that can come into contact with the side surface 222a of the spiral groove and the side surface 222b of the spiral groove. Further, the solid lubricating coating 242 may be provided also on the first pressure receiving surface of the first divided portion 240A and the second pressure receiving surface of the second divided portion 241A. The solid lubricant film 242 can be formed of, for example, boron fiber, carbon fiber, or the like.

  According to the third embodiment, the sliding resistance between the blade 24A and the spiral groove 22 can be reduced, and the first divided portion 240A, the second divided portion 241A, the low pressure side bottom surface 221a of the spiral groove, and the high pressure. The degree of contact with the side bottom surface 221b can be appropriately controlled and maintained, and a desired sealing function can be exhibited over a long period of time.

(Fourth embodiment)
In the fourth embodiment, a blade 24B, which is another form of the first embodiment, will be described with reference to FIG. In FIG. 9, the constituent elements having the same reference numerals as those in the drawing referred to in the first embodiment are the same elements, and the operational effects thereof are also the same. Hereinafter, different forms, operations, effects, and the like from the first embodiment will be described. FIG. 9 shows the relationship between the first divided portion 240B and the second divided portion 241B of the blade 24B and the spiral groove 22B at the highest position.

  As shown in FIG. 9, the first divided portion 240B has a curved surface that is recessed toward the cylinder 20 on the high-pressure side (or the second divided portion 241B side) of the tip portion facing the bottom surface 221B of the spiral groove. 1 pressure receiving surface 240Ba. The first pressure receiving surface 240Ba has a lower pressure side portion than a high pressure side portion so that the portion close to the side surface 222a of the spiral groove has a larger protruding amount from the cylinder 20 than the portion close to the second divided portion 241B. Also forms a protruding curved surface.

  The second divided portion 241B includes a second pressure receiving surface 241Ba that forms a curved surface that is recessed toward the cylinder 20 on the low pressure side (or the first divided portion 240B side) of the tip portion facing the bottom surface 221B of the spiral groove. . The second pressure receiving surface 241Ba has a portion on the high pressure side that is closer to the side of the spiral groove than the portion on the low pressure side so that the portion protruding from the cylinder 20 is larger than the portion near the first divided portion 240B. Also forms a protruding curved surface. When both the first pressure-receiving surface 240Ba and the second pressure-receiving surface 241Ba are combined, a curved surface that is recessed in a semi-cylindrical shape is formed.

  In a state where a space is formed between the tip portion of the blade 24B and the bottom surface 221B of the spiral groove from the state where the blade 24B sinks most with respect to the roller 21A, as shown in FIG. From the pressure PH of the working fluid that has entered, the first pressure receiving surface 240Ba has a component force PHx in a direction to move the first divided portion 240B away from the second divided portion 241B and a direction in which the first divided portion 240B is pushed toward the cylinder 20 side. The component force PHy comes to work.

  Accordingly, the first dividing portion 240B located on the low pressure side is pushed to the low pressure side by the component force PHx, so that the low pressure side surface of the first dividing portion 240B is in close contact with the side surface 222a of the spiral groove located on the low pressure side. become. The second divided portion 241B located on the high pressure side is pushed to the high pressure side by the component force PHx, and the side surface on the high pressure side of the second divided portion 241B is pushed to the side surface 222b of the spiral groove located on the high pressure side. It becomes like this. Such a form is similarly secured from the end of winding of the blade 24B to the end of winding, and each working chamber is reliably sealed. Even when the side surface of the second divided portion 241B and the side surface 222b of the spiral groove located on the high pressure side do not come into close contact with each other, the side surface of the first divided portion 240B and the side surface of the spiral groove on the low pressure side. Since 222a forms a seal structure, the low pressure side working chamber and the high pressure side working chamber can be shut off with the blade 24B interposed therebetween.

  Further, the bottom surface 221B of the spiral groove is formed in a plane that is parallel to the rotation shaft 210 of the roller and orthogonal to the direction in which the blade 24B protrudes. Therefore, when the blade 24B is most depressed with respect to the roller 21A, the first pressure receiving surface 240Ba and the second pressure receiving surface 241Ba do not contact the bottom surface 221B of the spiral groove, and a gap is formed between them. Will be.

(Fifth embodiment)
In the fifth embodiment, a blade 24C, which is another form of the first embodiment, will be described with reference to FIG. In FIG. 10, the components given the same reference numerals as those in the drawing referred to in the first embodiment are the same elements, and the operational effects thereof are also the same. Hereinafter, different forms, operations, effects, and the like from the first embodiment will be described. FIG. 10 shows the relationship between the first divided portion 240C and the second divided portion 241C of the blade 24C and the spiral groove 22B at the highest position.

  As shown in FIG. 10, the first divided portion 240C has a cylinder 20 side with respect to a low pressure side tip on the high pressure side (or the second divided portion 241C side) of the tip portion facing the bottom surface 221B of the spiral groove. A step that is recessed is formed. A surface (for example, a vertical surface) orthogonal to the rotation shaft 210 that connects the step and the tip on the low pressure side constitutes a first pressure receiving surface 240Ca.

  In the second divided portion 241C, a step is formed on the low pressure side (or the first divided portion 240C side) of the tip portion facing the bottom surface 221B of the spiral groove. Yes. A surface (for example, a vertical surface) perpendicular to the rotation shaft 210 that connects the step and the tip on the high pressure side constitutes a second pressure receiving surface 241Ca. The first pressure receiving surface 240Ca and the second pressure receiving surface 241Ca are in a relationship facing each other in the direction of the rotating shaft 210.

  In a state in which a space is formed between the tip portion of the blade 24C and the bottom surface 221B of the spiral groove from the state in which the blade 24C sinks most to the roller 21A, as shown in FIG. The pressure PH of the working fluid that has entered the spiral groove 22B acts on 240Ca. Accordingly, the first divided portion 240C located on the low pressure side is pushed to the low pressure side by the pressure PH so that the side surface on the low pressure side of the first divided portion 240C is in close contact with the side surface 222a of the spiral groove located on the low pressure side. Become.

  Further, the second divided portion 241C located on the high pressure side is pushed to the high pressure side by the pressure PH, and the side surface on the high pressure side of the second divided portion 241C is pushed to the side surface 222b of the spiral groove located on the high pressure side. become. Such a configuration is similarly ensured from the end of winding of the blade 24C to the end of winding, and each working chamber is reliably sealed. Even when the side surface of the second divided portion 241C and the side surface 222b of the spiral groove located on the high pressure side do not come into close contact with each other, the side surface of the first divided portion 240C and the side surface of the spiral groove on the low pressure side. Since 222a forms a seal structure, the low pressure side working chamber and the high pressure side working chamber can be shut off with the blade 24C interposed therebetween.

  Further, the bottom surface 221B of the spiral groove is formed in a plane that is parallel to the rotation shaft 210 of the roller and orthogonal to the direction in which the blade 24C protrudes. Therefore, in the state where the blade 24C sinks most with respect to the roller 21A, the first pressure receiving surface 240Ca and the second pressure receiving surface 241Ca and the bottom surface 221B of the spiral groove are not in contact, and a gap is formed between them. Will be.

(Other embodiments)
In the above-described embodiment, the preferred embodiment of the present invention has been described. However, the present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the spirit of the present invention. It is. The structure of the said embodiment is an illustration to the last, Comprising: The scope of the present invention is not limited to the range of these description. The scope of the present invention is indicated by the description of the scope of claims, and further includes meanings equivalent to the description of the scope of claims and all modifications within the scope.

  The first divided portions 240, 240A, 240B, and 240C and the second divided portions 241, 241A, 241B, and 241C in the above embodiment are portions that bisect not only the tip portion of the blade but also the entire longitudinal section of the blade. The 1st division part and the 2nd division part which are included in this invention are not limited to such a form. The 1st division part and the 2nd division part concerning the invention in this application should just be a form in which the tip part of the blade which counters the bottom of a spiral groove at least is divided into two. That is, with the form in which the tip part of the blade is divided into two forks, the fork is deformed so as to be separated from each other by the high-pressure fluid acting on the first pressure receiving surface and the first pressure receiving surface, and comes into contact with the spiral groove. It is sufficient that the low pressure side and the high pressure side of the compression chamber can be shut off with the blade interposed therebetween.

  The first pressure receiving surface and the second pressure receiving surface included in the present invention are not limited to the forms disclosed in the above embodiments. That is, the first pressure-receiving surface and the second pressure-receiving surface are configured such that when the high-pressure fluid acts on the tip of the first split portion and the tip of the second split portion, the first split portion and the second split portion are mutually connected. The shape is not limited to the above-described embodiment as long as the force that moves in the separating direction works.

DESCRIPTION OF SYMBOLS 1 ... Compressor, 2 ... Compression mechanism part, 3 ... Motor part, 20 ... Cylinder, 21, 21A ... Roller,
22, 22A ... spiral groove, 23 ... compression chamber, 24, 24A, 24B, 24C ... blade,
221, 221A ... bottom surface of spiral groove,
240, 240A, 240B, 240C ... 1st division part,
240a, 240Aa, 240Ba, 240Ca ... first pressure receiving surface,
241, 241A, 241B, 241C ... second dividing unit,
241a, 241Aa, 241Ba, 241Ca ... second pressure receiving surface

Claims (4)

A cylinder (20), a roller ( 21 ) provided eccentrically inside the cylinder, and having a spiral groove ( 22, 22A ) extending in a spiral shape on the outer peripheral surface, and a retractable fit in the spiral groove A compression mechanism portion (2) including a blade ( 24, 24A ), and a motor portion (3) for rotationally driving the roller, and spirally formed by the blade between the cylinder and the roller. A compressor (1) for compressing a working fluid in a compression chamber (23) formed in
The blade has a first divided portion ( 240 ) and a second divided portion ( 241 ) that are divided so that portions fitted into the spiral groove are aligned in the rotation axis direction of the roller,
Said first dividing section, the distal end portion facing the bottom surface of the spiral groove, force the first dividing unit by the pressure of the intruding working fluid in the helical groove in a direction away from the second splitting section A first pressure-receiving surface ( 240a ) that acts;
The second divided portion has a tip portion facing the bottom surface ( 221 ) of the spiral groove in a direction to move the second divided portion away from the first divided portion by the pressure of the working fluid that has entered the spiral groove. possess a second pressure receiving surface which force acts to (241a),
The first pressure receiving surface and the second pressure receiving surface are each formed by an inclined surface in which the side surface (222a, 222b) side of the spiral groove protrudes from the opposite side in the rotation axis direction,
A bottom surface of the spiral groove is formed in a shape along both of the first pressure receiving surface and the second pressure receiving surface, and the blade is formed by the blade on the first pressure receiving surface and the second pressure receiving surface. compressors you characterized by contacting the bottom surface of the spiral groove in the most sunken state with respect to the helical grooves. A cylinder (20), a roller (21, 21A) provided eccentrically inside the cylinder and having a spiral groove (22, 22A) extending in a spiral shape on the outer peripheral surface, and can appear and disappear in the spiral groove A compression mechanism part (2) including a blade (24, 24A) fitted in the motor, and a motor part (3) for rotationally driving the roller, and the blade between the cylinder and the roller. A compressor (1) for compressing a working fluid in a compression chamber (23) formed in a spiral shape,
The blade has a first divided portion (240, 240A) and a second divided portion (241, 241A) that are divided so that portions fitted in the spiral groove are aligned in the rotation axis direction of the roller. ,
The first divided portion moves the first divided portion away from the second divided portion at the tip portion facing the bottom surface (221, 221A) of the helical groove by the pressure of the working fluid that has entered the helical groove. Having a first pressure receiving surface (240a, 240Aa) on which a force acts in the direction;
In the second divided portion, a force acts on the tip portion facing the bottom surface of the spiral groove in a direction to move the second divided portion away from the first divided portion by the pressure of the working fluid that has entered the spiral groove. A second pressure receiving surface (241a, 241Aa)
The first pressure receiving surface and the second pressure receiving surface are each formed by an inclined surface in which the side surface (222a, 222b) side of the spiral groove protrudes from the opposite side in the rotation axis direction ,
Pressure of the first dividing unit and the second division unit, the well tip portion of the blade that faces the bottom surface of the spiral groove, you being a part which bisects the entire longitudinal section of the blade Reduction machine. The compressor according to claim 1 or 2 , wherein a solid lubricant film (223) is formed on a wall surface of the spiral groove (22A) in contact with the blade. The compressor according to claim 1 or 2 , wherein a solid lubricating film (242) is formed on a surface of the blade (24A).

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