JP2011220263A - Helical type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a helical type compressor capable of boosting the pressure of fluid to a required level appropriately.SOLUTION: An end 23a on the discharge side of a helical blade 23 that is fitted into a helical groove 22a of a rotor 22 is connected to a connection part 23b located at a section of the blade 23 that turns back from the end 23a by about one spire (by about 360°). Further, a reed valve (check valve) is provided which allows fluids in a compression room CR3 on the discharge side surrounded by a portion of the blade 23 that continues into the end 23a and the connection part 23b, an inner circumferential surface of a cylinder 21 and an outer circumferential surface of the rotor 22 only to flow from the compression room CR3 on the discharge side through a discharge hole 21a. This allows the pressure of the fluids to be appropriately boosted to the required level in the compression room CR3 on the discharge side, and allows the fluids to be discharged from the discharge hole 21a.

Description

  The present invention relates to a helical compressor that compresses and discharges a fluid by rotating eccentrically a rotor in which a spiral blade is inserted and retracted in a cylinder that forms a cylindrical space therein.

  2. Description of the Related Art Conventionally, a cylinder that forms a cylindrical space inside, a substantially cylindrical rotor that is eccentrically arranged inside the cylinder, and a helical blade that is removably fitted in a helical groove formed on the outer peripheral surface of the rotor Is known (for example, see Patent Document 1). In this type of helical compressor, a rotor in which a blade is fitted is eccentrically rotated in a cylinder, whereby fluid is sucked, compressed, and discharged.

  More specifically, the blade of the helical compressor is formed in a shape in which the interval between the side wall surfaces facing each other in the axial direction of the rotor is gradually reduced from one end side to the other end side in the axial direction of the rotor. . Further, in the helical compressor, a compression chamber for compressing fluid is formed by a space surrounded by the side wall surface of the blade that intersects the axial direction of the rotor, the inner peripheral surface of the cylinder, and the outer peripheral surface of the rotor.

  Therefore, when the rotor is eccentrically rotated in the cylinder, the compression chamber moves from one end side in the axial direction of the rotor to the other end side, and as the interval between the side wall surfaces facing in the axial direction of the rotor decreases, Reduce the volume. Thereby, in the helical compressor of patent document 1, the fluid suck | inhaled from the axial direction one end side of the rotor is compressed and discharged from the other end side.

JP-A-6-221286

  By the way, in the helical compressor of Patent Document 1, a compression chamber formed on one end side in the axial direction of the rotor (hereinafter referred to as suction side) is in communication with a fluid suction port (suction port) for sucking fluid. Cannot compress the fluid even if the rotor rotates. Similarly, while the compression chamber formed on the other axial end of the rotor (hereinafter referred to as the discharge side) communicates with the fluid discharge port (discharge port) for discharging the fluid, the rotor rotates. The fluid cannot be compressed.

  Therefore, the mechanical compression ratio in the helical compressor of Patent Document 1 is determined by the ratio between the volume when the compression chamber stops communicating with the fluid suction port and the volume immediately before the compression chamber communicates with the fluid discharge port. Is done. This will be described in detail with reference to FIGS.

  FIG. 9 shows an axial distance between opposing side wall surfaces of the blade 230 forming each compression chamber CR10, CR20, CR30, CR40 in the helical compressor 20 having the same configuration as that of Patent Document 1. FIG. More specifically, FIG. 9 shows a correspondence between a schematic axial sectional view of the helical compressor 20 and a graph in which the positions of the suction side wall surface and the discharge side wall surface of the blade 230 are developed. The relationship is illustrated.

  Further, as shown in FIG. 9, the blade 230 of the helical compressor 20 is formed in a spiral shape of 3 turns (1080 °). 9 shows a state in which the suction-side end portion of the blade 230 is immersed in the spiral groove of the rotor 220. Further, in the graph of FIG. 9, the starting position of the discharge-side side wall surface of the suction-side end portion of the blade 230 is set to a reference angle of 0 °, and the suction-side end surface of the blade 230 is the suction-side side wall surface. Is set to −360 ° which is delayed by one turn from the reference angle.

  As is apparent from the graph of FIG. 9, the positions of the side wall surface on the suction side and the side wall surface on the discharge side of the blade 230 change while drawing a similar locus with respect to the angle θ. Therefore, in the graph of FIG. 9, the positions of the suction side wall surface and the discharge side wall surface of the blade 230 are represented by a function f (θ) of the angle θ.

  10 is a BB cross-sectional view of the axial cross-sectional view of FIG. 9, and FIG. 11 is a radial distance H (θ between the inner peripheral surface of the cylinder 210 and the outer peripheral surface of the rotor 220 shown in FIG. ). The angle on the horizontal axis in FIG. 11 indicates the angle starting from the suction side end of the blade 230, as in the horizontal axis of the graph shown in FIG.

  First, as shown in FIG. 9, the suction side compression chamber CR10 formed on the most suction side includes a suction side wall surface positioned at −360 ° to 0 ° of the blade 230, an inner peripheral surface of the cylinder 210, and a rotor 220. And a space surrounded by a suction side lid member 2110 that closes the suction side of the cylinder 210. In the suction side compression chamber CR10, the fluid cannot be compressed even if the rotor 220 rotates because it communicates with the refrigerant suction port 2110a provided in the suction side lid member 2110.

  Next, the compression chamber CR20 formed adjacent to the suction side compression chamber CR10 and on the discharge side is a side wall surface on the discharge side and a side wall surface on the suction side, which is positioned at 0 ° to 360 ° of the blade 230, and the cylinder 210. A space surrounded by the inner peripheral surface and the outer peripheral surface of the rotor 220. Since the volume of the compression chamber CR20 is reduced with the rotation of the rotor 220, the fluid can be compressed.

  Further, the compression chamber CR30 formed on the discharge side next to the compression chamber CR20 includes a discharge side wall surface and a suction side wall surface, and an inner peripheral surface of the cylinder 210, which are positioned at 360 ° to 720 ° of the blade 230. A space surrounded by the outer peripheral surface of the rotor 220. Since the volume of the compression chamber CR30 is reduced with the rotation of the rotor 220 in the same manner as the compression chamber CR20, the fluid can be compressed.

  The volumes of the compression chambers CR20 and CR30 are shown in FIG. 11 as the distance f (θ + 360 °) −f (θ) between the opposing side wall surfaces of the blade 230 constituting the compression chambers CR20 and CR30 shown in FIG. By integrating the integrated value of the radial distance H (θ) between the outer peripheral surface of the rotor 220 and the inner peripheral surface of the cylinder 210 with the rotation angle of the rotor 220, the following equation can be obtained.

  However, as shown in FIG. 9, the discharge-side compression chamber CR40 formed next to the compression chamber CR30 and closest to the discharge side is the side wall surface on the discharge side positioned at 720 ° to 1080 ° of the blade 230, and the cylinder 210. The outer peripheral surface of the rotor 220, the outer peripheral surface of the rotor 220, and a discharge-side lid member 2120 that closes the discharge side of the cylinder 210. Since the compression chamber CR40 communicates with the refrigerant discharge port 2120a provided in the discharge-side lid member 2120, the fluid cannot be compressed even if the rotor 220 rotates.

  Therefore, the pressure of the fluid in the helical compressor 20 with respect to the rotation angle of the blade 230 changes as shown in FIG. FIG. 12 is a graph showing the pressure change of the fluid in the helical compressor 20 with respect to the rotation angle of the blade 230.

  In other words, in the helical compressor 20 having the same configuration as that of Patent Document 1, only two turns (0 ° to 720 °) out of the three blades 230 contribute to fluid compression. Therefore, the mechanical compression ratio in the helical compressor of Patent Document 1 is such that the compression chamber becomes a fluid discharge port when the compression chamber stops communicating with the fluid suction port (0 ° to 360 ° in FIG. 9). It is determined by the ratio with the volume immediately before the communication (360 ° to 720 ° in FIG. 9).

  For this reason, for example, when the helical compressor of Patent Document 1 is applied to a refrigeration cycle in which heat is exchanged between the refrigerant discharged from the compressor and the outside air to dissipate heat, the high-pressure side refrigerant pressure of the cycle with a decrease in the outside air temperature or the like Even if the operating conditions are low, there is a concern that unnecessarily high-pressure refrigerant is discharged from the compressor and the operating efficiency of the refrigeration cycle is greatly reduced.

  In view of the above points, an object of the present invention is to provide a helical compressor capable of appropriately boosting a fluid to a required pressure.

In order to achieve the above object, in the invention described in claim 1, a cylinder (21) that forms a cylindrical space inside, and an eccentric arrangement inside the cylinder (21), and a spiral shape on the outer peripheral surface thereof. A cylindrical rotor (22) formed with a spiral groove (22a) extending in the shape of a cylindrical groove (22a) and a spiral groove (22a) that can be projected and retracted, and its outer peripheral end contacting the inner peripheral surface of the cylinder (21) A helical blade (23) that forms a compression chamber (CR1, CR2, CR3) between the inner peripheral surface of the cylinder (21) and the outer peripheral surface of the rotor (22), and the rotor (22) The fluid sucked from one end side while moving the compression chamber (CR1, CR2, CR3) from one end side to the other end side in the axial direction of the rotor (22) by rotating eccentrically with respect to the central axis of (21). Compressing helica Be an expression compressor,
The end portion (23a) on the other end side of the blade (23) is connected to a connecting portion (23b) provided at a position on one end side of the end portion (23a) of the blade (23). (21) includes a discharge portion surrounded by a portion of the blade (23) connected to the end (23a) and the connecting portion (23b), the inner peripheral surface of the cylinder (21), and the outer peripheral surface of the rotor (22). Discharge hole (21a) for allowing fluid to flow out from the side compression chamber (CR3) is provided, and further allows fluid to flow in the direction of flowing out from the discharge side compression chamber (CR3) via the discharge hole (21a). It features a helical compressor with a check valve (27).

  According to this, since the end portion (23a) and the connecting portion (23b) on the other end side of the blade (23) are connected, the discharge side compression chamber (CR3) formed on the other end side is formed into a bag path shape. can do. Therefore, if the check valve (27) is closed and the discharge hole (21a) is kept closed, the fluid in the discharge side compression chamber (CR3) can be continuously compressed.

  On the other hand, since the fluid in the discharge side compression chamber (CR3) can flow out of the discharge hole (21a) by opening the check valve (27), after the check valve (27) is opened, the patent document As with the helical compressor 1, the fluid is not compressed even when the rotor (22) rotates. As a result, the fluid pressure can be appropriately increased to the required pressure without unnecessarily increasing the discharge fluid pressure.

  In the invention according to claim 2, in the helical compressor according to claim 1, the discharge hole (21a) is formed between the end portion (23a) and the connecting portion (23b) in the discharge side compression chamber (CR3). It is provided so that it may communicate with the vicinity of a connection part. According to this, if the state where the check valve (27) is closed and the discharge hole (21a) is closed is maintained, the fluid can be compressed until the pressure becomes the highest.

  In addition, the term “communicating in the vicinity” in this claim means that the discharge hole (21a) is adjacent to the connection portion between the end portion (23a) and the connection portion (23b) in the discharge side compression chamber (CR3). It means not only that it is opened, but also that it is opened at a position slightly away from the connecting part due to manufacturing errors and assembly reasons.

  According to a third aspect of the present invention, in the helical compressor according to the first or second aspect, the other end of the rotor (22) has a diameter smaller than the maximum outer diameter of the rotor (22). A small diameter portion (22d) is formed, and a ring member (22e) forming a part of the spiral groove (22a) is fixed to the small diameter portion (22d).

  According to this, the ring member (22e) can be fixed to the small diameter portion (22d) after the blade (23) is fitted into the spiral groove (22a) formed on the outer peripheral surface of the rotor (22). Therefore, the assembling property when the blade (23) is fitted into the rotor (22) can be improved.

  According to a fourth aspect of the present invention, in the helical compressor according to any one of the first to third aspects, one of the end portion (23a) and the connecting portion (23b) faces the other. A projecting portion (23c) is formed, and the projecting portion (23c) is fitted into an engagement hole (23d) provided on the other of the end portion (23a) and the connecting portion (23b), The terminal part (23a) and the connection part (23b) are connected.

  According to this, the assembling property when the blade (23) is fitted into the spiral groove (22a) can be improved. Furthermore, it is not necessary to form the blade (23) in which the end portion (23a) and the connecting portion (23b) are connected, and the blade (23) can be easily manufactured.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

It is a whole lineblock diagram of the refrigerating cycle to which the compressor of a 1st embodiment was applied. (A) is an axial sectional view of the compressor of the first embodiment, and (b) is a side view of (a). It is AA sectional drawing of FIG.2 (b). In the compressor of 1st Embodiment, it is explanatory drawing which shows the distance of the axial direction of the side wall surfaces which the braid | blade which forms each compression chamber opposes. It is a graph which shows the pressure change of the refrigerant | coolant in the compressor of 1st Embodiment. It is an axial sectional view of the compressor of the second embodiment. It is sectional drawing corresponding to FIG. 3 in the compressor of 2nd Embodiment. (A) is sectional drawing corresponding to FIG. 3 in the compressor of 3rd Embodiment, (b), (c) is sectional drawing which shows the modification. It is explanatory drawing which shows the distance of the axial direction of the side wall surfaces which the blade which forms each compression chamber in the prior art helical compressor opposes. It is BB sectional drawing of FIG. It is a graph which shows the change of the radial direction distance of the outer peripheral surface of a rotor and the internal peripheral surface of a cylinder in the helical compressor of a prior art. It is a graph which shows the pressure change of the refrigerant | coolant in the helical compressor of a prior art.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is an overall configuration diagram of a refrigeration cycle 1 to which a helical compressor (hereinafter simply referred to as a compressor) 2 of the present embodiment is applied. This refrigeration cycle 1 has a function of cooling indoor air blown into a room in an air conditioner that performs indoor air conditioning.

  More specifically, the refrigeration cycle 1 includes a compressor 2 that compresses and discharges the refrigerant, a radiator 3 that radiates heat by exchanging heat between the refrigerant discharged from the compressor 2 and the outside air, and an expansion that decompresses and expands the refrigerant that flows out of the radiator 3. A well-known vapor compression refrigeration cycle configured by annularly connecting an evaporator 5 that exhibits an endothermic effect by evaporating the valve 4 and the refrigerant depressurized by the expansion valve 4 to cool indoor blown air. It is.

  Next, based on FIG. 2, 3, the detailed structure of the compressor 2 of this embodiment is demonstrated. Fig.2 (a) is an axial sectional view of the compressor 2, and FIG.2 (b) is a side view of Fig.2 (a). 3 is a cross-sectional view taken along the line AA of FIG. 2B, that is, a development view of a cylindrical outer peripheral surface of the rotor 22 and the blade 23, which will be described later. The vicinity of the end portion 23a on the side is shown.

  As shown in FIG. 2, the compressor 2 includes a cylinder 21, a rotor 22 disposed inside the cylinder 21, a spiral blade 23 that is removably fitted in a spiral groove 22 a of the rotor 22, an electric motor 24, an electric motor A shaft 25 or the like for transmitting the rotational driving force of the motor 24 to the rotor 22 is provided.

  The cylinder 21 is formed of a substantially cylindrical metal, and constitutes an outer shell of the compressor 2 and forms a columnar space for accommodating the rotor 22, the blade 23, the shaft 25 and the like therein. Further, the inner peripheral surface of the cylinder 21 forms a plurality of compression chambers CR for compressing a refrigerant that is a fluid together with the rotor 22 and the blade 23 as will be described later.

  One open end of the cylinder 21 formed in a cylindrical shape is closed by a suction side lid member 211 formed of a disk-shaped metal. The suction-side lid member 211 is provided with a through-hole penetrating the front and back, and the through-hole serves as a suction-side compression chamber that is positioned closest to the suction-side lid member 211 among the plurality of compression chambers CR. It functions as a refrigerant suction port 211a to be sucked into CR1.

  The other open end of the cylinder 21 is also closed by a discharge side lid member 212 made of a disk-shaped metal. A through hole 212 a through which the shaft 25 passes is provided at the center of the discharge side lid member 212. A seal member (lip seal) (not shown) is disposed in the through hole 212a, thereby preventing the refrigerant from leaking from the gap between the shaft 25 and the through hole 212a.

  The shaft 25 has a rotation center axis extending coaxially with the center axis of the cylinder 21 and is rotated by a through hole 212a and a bearing portion 211b provided at the center portion of the suction side compression chamber CR1 side surface of the suction side lid member 211. Supported as possible. Further, an eccentric portion 25 a that is eccentric with respect to the rotation center axis of the shaft 25 is formed at the axial central portion of the shaft 25.

  The rotor 22 is formed of a columnar (or cylindrical) metal in which a spiral groove 22a extending in a spiral shape is formed on the outer peripheral surface thereof, and an eccentric portion 25a of the shaft 25 is rotatably inserted into a central portion thereof. An insertion hole 22b is provided. The central axis of the insertion hole 22b extends coaxially with the central axis of the rotor 22 and the central axis of the eccentric portion 25a of the shaft 25.

  On the other hand, as described above, since the rotation center axis of the shaft 25 and the center axis of the cylinder 21 are arranged coaxially, the center axis of the cylinder 21 and the center axis of the eccentric portion 25a (center axis of the rotor 22) are mutually connected. They are arranged in parallel at regular intervals. That is, the rotor 22 is arranged eccentrically inside the cylinder 21.

  Further, a pin 22c protruding toward the discharge side cover member 212 is fixed to an end portion of the rotor 22 on the discharge side cover member 212 side by a fixing means such as press fitting, and the discharge side cover member 212 has a pin 22c. A circular hole 212b that accommodates the end and restricts the movable range of the pin 22c is formed.

  The pin 22c and the circular hole 212b constitute a so-called pin-hole type anti-rotation mechanism. Therefore, even if the shaft 25 rotates, the rotor 22 revolves around the center of rotation of the shaft 25 without rotating around the eccentric portion 25a of the shaft 25. The details of the spiral groove 22a formed on the outer peripheral surface of the rotor 22 will be described later.

  The blade 23 is formed of a spiral resin, and is fitted in a spiral groove 22 a formed on the outer peripheral surface of the rotor 22 so as to be able to protrude and retract, and between the inner peripheral surface of the cylinder 21 and the outer peripheral surface of the rotor 22. A plurality of compression chambers CR are formed.

  More specifically, an elastic member (not shown) is disposed between the end surface of the blade 23 on the rotor 22 side and the bottom surface of the spiral groove 22a of the rotor, and the blade 23 is moved by the elastic force of the elastic member. It protrudes from the spiral groove 22a until the outer peripheral end portion contacts the inner peripheral surface of the cylinder 21.

  As a result, a portion of the blade 23 protruding from the spiral groove 22 a and intersecting in the axial direction of the rotor 22, a space surrounded by the inner peripheral surface of the cylinder 21, and the outer peripheral surface of the rotor 22, The compression chamber CR is formed. In addition, the blade 23 of this embodiment is formed in a spiral shape of about 3 turns (1080 °).

  Further, the blade 23 is configured such that the interval between the side wall surfaces facing each other in the axial direction of the rotor 22 extends from the suction side lid member 211 side (hereinafter referred to as the suction side), which is one axial side of the rotor 22, to the other axial end of the rotor 22. It is formed in a spiral shape that gradually decreases toward the discharge side lid member 212 side (hereinafter referred to as the discharge side).

  Therefore, when the rotor 22 is eccentrically rotated in the cylinder 21, each compression chamber CR moves from the suction side toward the discharge side, and as the interval between the side wall surfaces facing in the axial direction of the rotor 22 decreases. , Reduce its volume. As a result, the compressor 2 compresses the refrigerant sucked from the suction side of the rotor 22.

  Further, as shown in FIG. 3, the blade 23 of the present embodiment includes a connecting portion 23 b provided at a portion where the discharge-side end portion 23 a of the rotor 22 is positioned on the suction side of the blade 23 relative to the end portion. It is connected to. More specifically, the end portion 23a of the blade 23 of the present embodiment is connected to a connecting portion 23b positioned at a position returned from the end portion 23a by about one turn (about 360 °).

  Here, the detailed shape of the spiral groove 22a formed on the outer peripheral surface of the rotor 22 will be described. Since the spiral groove 22a is a groove into which the blade 23 can be inserted and retracted, the spiral groove 22a is formed in a shape that matches the shape of the blade 23 described above. That is, the spiral groove 22a also has a spiral shape in which the interval gradually decreases from the suction side to the discharge side of the rotor 22, and is formed in a shape that can accommodate the connected end portion 23a and the connection portion 23b. .

  Further, as shown in FIG. 2, the cylindrical wall surface of the cylinder 21 of the present embodiment includes a portion of the blade 23 that is continuous with the end portion 23 a and the connecting portion 23 b, an inner peripheral surface of the cylinder 21, and an outer peripheral surface of the rotor 22. Is provided with a discharge hole 21a that functions as a discharge port for allowing the refrigerant to flow out of the discharge side compression chamber CR3 surrounded by. The discharge side compression chamber CR3 is a compression chamber positioned closest to the discharge side lid member 212 among the plurality of compression chambers CR.

  The discharge hole 21a is provided so as to pass through the inner peripheral surface and the outer peripheral surface of the cylinder 21, as shown by a broken-line hole in FIG. 3, and the end portion of the blade 23 in the discharge-side compression chamber CR3. It is provided so that it may communicate with the vicinity of the connection part of 23a and the connection part 23b. In other words, the discharge hole 21a is opened so as to be adjacent to the connection portion between the end portion 23a and the connection portion 23b in the discharge side compression chamber CR3.

  More specifically, the discharge hole 21a is provided so as to communicate with the position where the refrigerant is at the highest pressure in the discharge side compression chamber CR3 when the state where the discharge hole 21a is closed is maintained. .

  Further, a case 26 that constitutes a discharge chamber 26 a of the refrigerant flowing out from the discharge hole 21 a is joined to the outer peripheral surface of the cylinder 21. A reed valve 27 that functions as a check valve that only allows refrigerant to flow from the discharge side compression chamber CR3 to the discharge chamber 26a side through the discharge hole 21a is disposed inside the case 26. Further, the case 26 is provided with a refrigerant discharge port 26b through which the refrigerant flows out from the discharge chamber 26a to the radiator 2 side shown in FIG.

  The electric motor 24 outputs a rotational driving force for rotating the rotor 22 when supplied with electric power, and may employ either a direct current motor or an alternating current motor. Furthermore, the rotation speed of the electric motor 24 is controlled by a control signal output from an air conditioning control device (not shown). The air conditioning control device includes a known microcomputer including a CPU, a ROM, a RAM, and the like and peripheral circuits thereof.

  Next, the operation of the compressor 2 and the refrigeration cycle 1 configured as described above will be described. When the electric motor 24 is rotated by a control signal output from the air conditioning control device, a rotational driving force is transmitted to the rotor 22 via the shaft 25, and the rotor 22 rotates eccentrically in the cylinder 21. Accordingly, the refrigerant is sucked into the cylinder 21 (specifically, the suction side compression chamber CR1) through the refrigerant suction port 211a.

  The refrigerant sucked into the cylinder 21 is compressed in the compression chamber CR that moves while reducing the volume from the suction side to the discharge side of the rotor 22 as the rotor 22 rotates. When the refrigerant pressure in the discharge side compression chamber CR3 becomes equal to or higher than the high pressure side refrigerant pressure of the cycle, the reed valve 27 is opened, and the refrigerant in the discharge side compression chamber CR3 flows into the discharge chamber 26a through the discharge hole 21a. To do.

  The high-pressure side refrigerant pressure of the cycle is a refrigerant pressure in a range from the refrigerant discharge port 26b of the compressor 2 to the inlet of the expansion valve 4, and is an air conditioning heat load (for example, outside temperature, evaporator) of the refrigeration cycle 1. 5 changes due to fluctuations in the refrigerant evaporation temperature.

  The refrigerant that has flowed into the discharge chamber 26a flows into the radiator 3 through the refrigerant discharge port 26b, and is cooled and condensed by exchanging heat with the outside air. The refrigerant flowing out of the radiator 3 is decompressed and expanded by the expansion valve 4 and flows into the evaporator 5. At this time, the opening degree of the expansion valve 4 is adjusted so that the degree of superheat of the refrigerant flowing out of the evaporator 5 falls within a predetermined range.

  The refrigerant flowing into the evaporator 5 absorbs heat from the indoor air and evaporates. Thereby, indoor ventilation air is cooled. The refrigerant flowing out of the evaporator 5 is sucked into the cylinder 21 through the refrigerant suction port 211a of the compressor 2 and compressed again.

  Next, the outstanding effect of the compressor 2 of this embodiment is demonstrated using FIG. FIG. 4 is an explanatory diagram showing the axial distance of the opposing side wall surfaces of the blades 23 forming the compression chambers CR1, CR2, and CR3 in the compressor 2 of the present embodiment. 9 corresponds to FIG. FIG. 5 is a graph showing the pressure change of the refrigerant in the compressor 2 with respect to the rotation angle of the blade 23, and corresponds to FIG.

  In the compressor 2 of the present embodiment, since the discharge-side end portion 23a and the connecting portion 23b of the blade 23 are connected, the discharge-side compression chamber CR3 positioned at the most discharge side is closed by the discharge hole 21a. In the case where the refrigerant is present, it can be formed into a bag path shape in which the refrigerant cannot flow out.

  Accordingly, as shown in FIG. 4, the discharge side compression chamber CR3 of the compressor 2 of the present embodiment includes the discharge side wall surface and the suction side wall surface, which are positioned at 360 ° to 720 ° of the blade 23, and the cylinder 21. It is formed by a space surrounded by the inner peripheral surface and the outer peripheral surface of the rotor 22. In the discharge side compression chamber CR3, the refrigerant can be continuously compressed as long as the reed valve 27 is closed and the discharge hole 21a is closed.

  On the other hand, since the refrigerant in the discharge side compression chamber CR3 can flow out from the discharge hole 21a by opening the reed valve 27, after the reed valve 27 is opened, the rotor 22 rotates as in the prior art. Even the refrigerant is not compressed. Therefore, as shown in FIG. 5, the discharge pressure can be changed in accordance with the conditions for opening the reed valve 27.

  As a result, the refrigerant pressure discharged from the compressor 2 is not unnecessarily increased, and the refrigerant can be appropriately boosted to the required pressure.

  Furthermore, since the discharge hole 21a is provided so as to communicate with the vicinity of the connection portion between the end portion 23a and the connection portion 23b in the discharge side compression chamber CR3, the state where the discharge hole 21a is closed is maintained. In some cases, the refrigerant can be compressed until it reaches the highest pressure. Therefore, the refrigerant discharge pressure can be changed in a wide range.

(Second Embodiment)
In the first embodiment, an example in which the rotor 22 is configured by a columnar (or cylindrical) metal member has been described. However, in the present embodiment, an example in which the configuration of the rotor 22 is changed as illustrated in FIGS. Will be explained.

  FIG. 6 is a sectional view in the axial direction of the compressor 2 of the present embodiment, and corresponds to FIG. 2A of the first embodiment. FIG. 7 is a drawing corresponding to FIG. 3 of the first embodiment. 6 and 7, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals. The same applies to the following drawings.

  Specifically, a small-diameter portion 22d having a diameter smaller than the maximum outer diameter of the rotor 22 is formed at the discharge-side end portion of the rotor 22 of the present embodiment, and one spiral groove 22a is formed in the small-diameter portion 22d. A rotor 22 having the same shape as that of the first embodiment is configured by fixing an annular ring member 22e forming a portion by press fitting or the like.

  The small-diameter portion 22d is provided in a range that reaches a portion returned from the end portion 23a on the discharge side of the blade 23 by one turn (about 360 °) (that is, a connecting portion between the end portion 23a and the connecting portion 23b). Yes. Accordingly, the ring member 22e forms a side wall surface of the spiral groove 22a that extends from the discharge-side end portion 23a of the blade 23 to the connecting portion between the end portion 23a and the connecting portion 23b.

  Other configurations and operations are the same as those in the first embodiment. Therefore, the compressor 2 of the present embodiment can achieve the same effects as those of the first embodiment. Furthermore, by configuring the rotor 22 as in the present embodiment, the ring member 22e can be fixed to the small diameter portion 22d after the blade 23 is fitted in the spiral groove 22a formed on the outer peripheral surface of the rotor 22. Therefore, the assembling property when the blade 23 is fitted into the spiral groove 22a of the rotor 22 can be improved.

(Third embodiment)
In the first embodiment, the example in which the blade 23 is formed in a state where the tip portion 23a and the connecting portion 23b are connected in advance has been described. However, in the present embodiment, as shown in FIG. An example in which the blade 23 formed in a state where the portion 23a and the connecting portion 23b are separated will be described. FIG. 8 is a drawing corresponding to FIG. 3 of the first embodiment.

  Specifically, as shown in FIG. 8A, a protrusion 23c protruding toward the connecting portion 23b is formed at the discharge-side end portion 23a of the blade 23 of the present embodiment. The end portion 23a and the connecting portion 23b are connected by fitting the portion 23c into an engaging hole 23d provided in the connecting portion 23b.

  Other configurations and operations are the same as those in the first embodiment. Therefore, the compressor 2 of the present embodiment can achieve the same effects as those of the first embodiment. Further, by configuring the blade 23 as in the present embodiment, it is possible to improve the assembling property when the blade 23 is fitted into the spiral groove 22a. Further, when the blade 23 is manufactured, it is not necessary to form a structure in which the end portion 23a and the connecting portion 23b are connected, and the blade 23 can be easily manufactured.

  In the above example, the example in which the projecting portion 23c is formed in the end portion 23a and the engagement hole 23d is formed in the connecting portion 23b has been described. However, as shown in FIG. Alternatively, the protruding portion 23c may be formed in the connecting portion 23b, and the engaging hole 23d may be formed in the end portion 23a. Further, as shown in FIG. 8C, the position where the protrusion 23c is formed may be disposed in the vicinity of the discharge side compression chamber CR3, or may be disposed on the side away from the discharge side compression chamber CR3. Good. Moreover, the blade 23 of this embodiment is applicable also to the compressor 2 of 2nd Embodiment.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention.

  In the above-described embodiment, an example in which the helical compressor of the present invention is applied to a refrigeration cycle for an air conditioner has been described. It is extremely effective when applied to a vehicle refrigeration cycle apparatus that is likely to fluctuate. Furthermore, the helical compressor of the present invention is widely applicable as a compressor that compresses various fluids.

  Moreover, although the above-mentioned embodiment demonstrated the example which employ | adopted the reed valve 27 as a non-return valve, a non-return valve is not limited to this. Various types of mechanisms can be adopted as long as the mechanism only allows the fluid (refrigerant) to flow from the discharge side compression chamber CR3 through the discharge hole 21a. For example, when the discharge hole 21a is opened and closed by a mechanical mechanism as in this embodiment, a ball valve type or pope valve type check valve may be employed.

  Further, an electrical control is provided by detecting an inlet-side fluid pressure and an outlet-side fluid pressure of the discharge hole 21a and opening / closing a valve that opens only when the inlet-side fluid pressure becomes higher than the outlet-side fluid pressure. Thus, a mechanism that only allows the fluid to flow in the direction of flowing out from the discharge side compression chamber CR3 through the discharge hole 21a may be realized.

  In the above-described embodiment, the example in which the number of turns of the spiral groove 22a of the blade 23 and the rotor 22 is three has been described. However, the number of turns of the spiral groove 22a of the blade 23 and the rotor 22 is not limited thereto.

21 Cylinder 21a Discharge hole 22 Rotor 22a Spiral groove 22d Small diameter portion 22e Ring member 23 Blade 23a End portion 23b Connection portion 23c Projection portion 23d Engagement portion 27 Check valve

Claims (4)

A cylinder (21) forming a cylindrical space inside;
A cylindrical rotor (22) that is eccentrically arranged inside the cylinder (21) and in which a spiral groove (22a) extending spirally is formed on the outer peripheral surface thereof;
The spiral groove (22a) is slidably fitted in and the outer peripheral end thereof is in contact with the inner peripheral surface of the cylinder (21), whereby the inner peripheral surface of the cylinder (21) and the outer periphery of the rotor (22). A spiral blade (23) that forms a compression chamber (CR1, CR2, CR3) with the surface;
By rotating the rotor (22) eccentrically with respect to the central axis of the cylinder (21), the compression chambers (CR1, CR2, CR3) are moved from one end side to the other end side in the axial direction of the rotor (22). A helical compressor that compresses the fluid sucked from the one end side,
The end portion (23a) on the other end side of the blade (23) is connected to a connecting portion (23b) provided at a position closer to the one end side than the end portion (23a) of the blade (23). Has been
The cylinder (21) includes a portion of the blade (23) connected to the end portion (23a) and the connecting portion (23b), an inner peripheral surface of the cylinder (21), and a rotor (22). A discharge hole (21a) for allowing the fluid to flow out from the discharge side compression chamber (CR3) surrounded by the outer peripheral surface is provided,
The helical compressor further comprises a check valve (27) that allows the fluid to flow from the discharge side compression chamber (CR3) in a direction of flowing out through the discharge hole (21a).   The discharge hole (21a) is provided so as to communicate with the vicinity of the connection portion between the end portion (23a) and the connection portion (23b) in the discharge side compression chamber (CR3). The helical compressor according to claim 1. The end on the other end side of the rotor (22) is a small diameter portion (22d) having a diameter smaller than the maximum outer diameter of the rotor (22),
The helical compressor according to claim 1 or 2, wherein a ring member (22e) forming a part of the spiral groove (22a) is fixed to the small diameter portion (22d). One of the end portion (23a) and the connecting portion (23b) is formed with a protruding portion (23c) protruding toward the other,
The protruding portion (23c) is fitted into an engagement hole (23d) provided on the other of the end portion (23a) and the connecting portion (23b), so that the end portion (23a) and the connecting portion ( The helical compressor according to any one of claims 1 to 3, wherein 23b) is connected.

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