JP4951586B2 - Scroll fluid machinery - Google Patents

Description

  The present invention relates to a scroll fluid machine provided with a revolving pressure assisting member that presses a revolving scroll member against a fixed scroll member with back pressure and assists the pressing on the back surface of the revolving scroll member. The present invention relates to a means for avoiding an abnormal increase in back pressure that occurs under circumstances.

  A conventional scroll fluid machine is a scroll fluid machine that operates while applying a back pressure, which is an intermediate pressure, to the back of the orbiting scroll member and pressing the orbiting scroll member against the fixed scroll member. In order to make a transition from the previous transient operation to the regular operation in a short time, there is one provided with a turning press auxiliary member that urges the turning scroll member toward the fixed scroll member during the transient operation (for example, Patent Document 1). reference). And in this prior art, the urging | biasing force to the turning scroll member of a turning press auxiliary | assistant member is generated with the discharge pressure led through the auxiliary member seal to the anti-revolving scroll member side.

JP 2007-138828 A

  With the scroll fluid machine described in Patent Document 1, it is possible to shorten the transition time from non-regular operation with low back pressure to regular operation. However, in the case of non-regular operation where the back pressure rises above the discharge pressure for some reason, such as when oil that is in a condition where the refrigerant is in a two-phase region is introduced into the back pressure chamber by a refrigerant compressor, the operation shifts to regular operation. In other words, the scroll members may be pressed with an excessive force and the sliding surface may be damaged. Further, the auxiliary member seal is crushed and the sealing performance is deteriorated. As a result, the back pressure chamber and the discharge space are communicated with each other, which may hinder the operation as a fluid machine. Furthermore, in the case of a differential pressure oil supply type in which oil supply to the bearing is performed by the differential pressure between the back pressure and the discharge pressure, the oil supply to the bearing is not performed and the bearing may be damaged.

  It is an object of the present invention to provide a scroll fluid machine that quickly adjusts a back pressure to an appropriate value side when a back pressure is high with respect to a turning press auxiliary member and an auxiliary member seal, which are countermeasures when the back pressure is low. And

  In order to solve the above-described problems, a scroll fluid mechanism according to the present invention is provided on a fixed scroll member, a turning scroll member that forms a compression chamber in cooperation with the fixed scroll member, and a back side of the turning scroll member. A back pressure chamber, back pressure control means for controlling the pressure of the back pressure chamber so as to press the orbiting scroll member against the fixed scroll member, and an orbiting pressure assist provided in opposition to the rear surface of the orbiting scroll member and movable in the axial direction. The auxiliary member back chamber, which is positioned on the opposite side of the orbiting scroll member with respect to the orbiting scroll auxiliary member and into which the discharge pressure is introduced, and the auxiliary member rear chamber and the back pressure chamber are blocked and movable in the axial direction. And an auxiliary member seal that presses the turning pressing auxiliary member toward the orbiting scroll member by the discharge pressure in the auxiliary member rear chamber, and the auxiliary member seal includes the back pressure chamber and the auxiliary member rear surface. Having an opening communicating and.

  ADVANTAGE OF THE INVENTION According to this invention, when back pressure is high, the scroll fluid machine which adjusts back pressure to the appropriate value side rapidly can be provided.

  Embodiments of a scroll fluid machine according to the present invention will be described below with reference to the drawings.

  A first embodiment of a scroll fluid machine according to the present invention will be described with reference to FIGS. FIG. 1 is a longitudinal sectional view of a scroll fluid machine. FIG. 2 is a plan view of the fixed scroll member on the spiral body side. FIG. 3 is a longitudinal sectional view of the orbiting scroll member, and FIG. 4 is a rear view of the orbiting scroll member. FIG. 5 is a top view of the frame. FIG. 6 is a longitudinal sectional view of a turning press assisting member which is a main part of the scroll fluid machine according to the present invention, and FIG. 7 is a top view of the turning press assisting member. FIG. 8 is a top view of the auxiliary member seal, and FIG. 9 is a longitudinal sectional view of the auxiliary member seal. 10 to 18 are enlarged views of a longitudinal sectional view (P portion in FIG. 1) of the turning pressing auxiliary member. FIGS. 10 to 12 show the progress of the familiarity of the familiarity layer. FIG. 10 shows during assembly or before familiarization and before startup, FIG. 11 shows familiarity operation, and FIG. 12 shows familiarity and regular operation. Show. FIG. 13 to FIG. 16 show the transition from transient operation to normal operation at startup, FIG. 13 is before startup when there is no back space before startup, and FIG. 14 is startup when there is back space before startup. Immediately after that, FIG. 15 shows after the back pressure increase in the case where the back space exists before the start, and FIG. 16 shows the auxiliary member seal after the rise in the case where the back space exists before the start. 17 and 18 show the transition from the case where the back pressure becomes higher than the discharge pressure to the normal operation, and FIG. 17 shows the state immediately after the start of the rear space formation when the back pressure becomes equal to or higher than the discharge pressure. Shows a state where the turning pressure assisting member and the assisting member seal are lowered and the back pressure is lowered when the back pressure becomes equal to or higher than the discharge pressure.

  Reference numeral 1 denotes a fixed scroll member, which includes a fixed spiral body 1a and a fixed end plate 1b each having an asymmetric tooth profile. The fixed spiral body 1a and the fixed end plate 1b may be symmetrical teeth. The fixed scroll member 1 forms a compression chamber in cooperation with an orbiting scroll member 2 described later. The tooth bottom surface of the fixed scroll member 1 is provided with two pairs of bypass holes 1c, and each is provided with a bypass valve 110. Thereby, over-compression suppression and liquid compression are avoided. Furthermore, the back pressure is optimized under a wide range of conditions by combining a back pressure control valve 100 described later. In addition, an outflow groove 1 d that communicates with the inner periphery of the fixed spiral body 1 a is provided, and an outflow hole 100 a that is an outlet from the back pressure control valve 100 is opened there.

  The back pressure control valve 100 includes a compressed valve spring 100b, a valve body 100c, and a valve cap 100d. The back pressure control valve 100 allows oil under discharge pressure generated during operation and fluid dissolved therein to flow into the back pressure chamber 4 on the back side of the orbiting scroll member 2 through the gap between the main bearing 15a and the orbiting bearing 2c. By doing this, it is a valve that releases the pressure that rises due to gasification and the like. Further, since the fluid is guided to the back pressure chamber 4 by the gap between the swing bearing 2c and the main bearing 15a, the both bearing gaps become the swing back inflow path. The back pressure control means sets a constant value corresponding to the compression amount of the valve spring 100b to the pressure at the opening end of the outflow hole 100a (generally, a constant multiple of the suction pressure) so as to press the orbiting scroll member 2 against the fixed scroll member. The back pressure is controlled by the added pressure.

  A revolving scroll member 2 includes a revolving spiral body 2a and a revolving end plate 2b. A conforming layer 2h that wears when sliding occurs under a large load is formed on the swivel sliding surface that is the upper surface of the swivel end plate 2b and the surface of the swirl spiral body 2a (see FIGS. 3 and 10 to 18). The thickness is exaggerated to illustrate the conforming layer (the actual thickness is the level of the gap caused by the shape error when the two scroll members are engaged). The conforming layer 2h is formed by processing the material surface of the orbiting scroll member 2. The conformable layer 2h includes an easily conformable layer 2h1 which is formed by being deposited from the surface of the material, and an unacceptable layer 2h2 which is formed by eroding the material surface and is difficult to conform. Therefore, the familiarity to the original material surface easily proceeds, but the further familiarization becomes difficult, and the surface after the familiarization is approximately near the original material surface. Since it can be estimated to what extent the dimensions after familiarization will be, there is a feature that the management of the dimensions is easy. In the case of the orbiting scroll member made of cast iron, there is a manganese phosphate coating as an example of such an erosion precipitation type familiar layer. The conforming layer may be provided on the surface of the fixed scroll member 1 facing the orbiting scroll member 2 or may be provided on both members. Further, in order to form a conforming layer 2h on the surface of the swivel sliding surface and the swirl spiral body 2a, which is the upper surface of the swivel end plate 2b, the conformal layer is provided on the entire surface except the bearing surface of the swivel bearing 2c, Only the back surface 2j can forcibly remove the conformable layer. On the orbiting back side, a balance digging 2y for adjusting the center of gravity of the orbiting Oldham groove 2k and the orbiting scroll member on the orbiting bearing shaft is provided.

  The fixed scroll member 1 and the orbiting scroll member 2 are engaged with each other, and the eccentric pin 9a of the crankshaft 9 supported by the frame 15 is inserted into the orbiting bearing 2c. Between the frame 15 and the orbiting scroll member 2, the orbiting pressing auxiliary member 3 and the Oldham ring 16 are arranged. At this time, an annular seal insertion groove 15b is provided on the side opposite to the orbiting scroll member of the orbiting pressing auxiliary member 3, and an annular seal as the auxiliary member seal 11 is inserted into the seal insertion groove 15b. Further, the key portion of the Oldham ring 16 is inserted into the orbiting Oldham groove 2 k of the orbiting scroll member 2 and the frame Oldham groove 15 k of the frame 15. The scroll fluid machine further includes a motor 17 that drives the crankshaft 9, a suction pipe 18 that takes in the fluid, and a discharge pipe 19 that discharges the compressed fluid. In this embodiment, the axial direction of the crankshaft is the axial direction of the scroll fluid machine.

  The flow of the compressed fluid in the scroll fluid machine will be described. The fluid that has flowed in from the suction pipe 18 flows into the suction chamber 6 (see FIG. 2), and is then compressed in the compression chamber 200 formed by the fixed scroll member 1 and the orbiting scroll member 2. The compression chamber 200 is formed by rotating the crankshaft 9 by the motor 17 and causing the orbiting scroll member 2 to revolve without being rotated by the Oldham ring 16. Thereafter, the fluid compressed in the compression chamber 200 is discharged into the case 20 above the fixed scroll member 1, fills the case 20, and then flows out of the fluid machine from the discharge pipe 19 on the side surface of the case 20. As a result, the inside of the case 20 becomes a discharge pressure.

  Next, the flow of oil in the scroll fluid machine will be described. In the differential pressure oil supply system, the oil of the scroll fluid machine uses the pressure difference between the discharge pressure in the case 20 and the back pressure in the back pressure chamber 4 and passes from the oil storage chamber 5 through the oil supply pipe 10 and the oil supply hole 9b. After being supplied to the slewing bearing 2 c and the main bearing 15 a, it flows into the back pressure chamber 4. Then, it passes through the back pressure control valve 100 and flows into the compression chamber 200 and the suction chamber 6 from the outflow hole 100a (for details, refer to the description of the back pressure control valve). The oil flowing into the compression chamber 200 and the suction chamber 6 is pressurized together with the compressed fluid while sealing the compression chamber 200 and is discharged into the case 20. Therefore, most of the oil is separated from the compressed fluid and collected in the oil storage chamber 5 below the case 20.

  Next, the structure and arrangement of the turning pressing auxiliary member and auxiliary member seal in the present embodiment will be described with reference to FIGS. The turning pressing auxiliary member 3 has a pressing auxiliary plate portion 3x whose main body has an annular plate shape, and rises from the turning regulating surface 3a by the same dimension as the thickness of the turning end plate 2b at the outer periphery. The protrusion 3b is provided. The thickness of the orbiting scroll material is equal to the thickness (T value in FIG. 10) up to the conformable difficult layer 2h2 after the conformable layer 2h is formed. Further, a plurality of pressing portion through holes 3c are provided in the pressing auxiliary plate portion 3x. The opening position of the pressing portion through hole 3c on the turning regulation surface 3a side is formed in a polishing groove 3y provided as a relief when the turning regulation surface 3a is polished, and the back surface side is opened to a position where the auxiliary member seal 11 is pressed. . Further, the auxiliary member seal 11 has a seal pressing portion 11e whose main body has an annular plate shape, and includes seal protrusions 11a on the inner peripheral side and the outer peripheral side of the lower surface of the seal pressing portion 11e. The shape of the auxiliary member seal 11 is not such an annular shape, and a plurality of auxiliary member seals 11 each having a disk-like seal pressing portion may be provided. A plurality of seal holes 11c penetrating the seal pressing portion 11e are provided. A seal hole 11c formed in the seal pressing portion 11e is formed so as to penetrate the seal pressing portion 11e from the back pressure chamber toward the turning pressing auxiliary member. As will be described later, the back pressure chamber and the auxiliary member back chamber are formed. Do not communicate with the opening.

  The arrangement of the turning pressing auxiliary member 3 and the auxiliary member seal 11 will be described. First, the auxiliary member seal 11 is inserted into the seal insertion groove 15 b provided on the bottom surface of the frame 15 to form the auxiliary member back chamber 8. At this time, the width dimension is determined so that the seal protrusion 11a slides lightly with the side surface of the seal insertion groove 15b. Further, since the length of the seal protrusion 11a is smaller than the depth of the seal insertion groove 15b (because the height of the seal insertion groove 15b is lower than the height of the auxiliary member seal), the auxiliary member seal is inserted into the seal insertion groove 15b. 11 enters. Furthermore, the turning pressing auxiliary member 3 is disposed on the auxiliary member seal 11 so as to face the seal pressing portion 11e. Since the auxiliary member seal 11 has entered the seal insertion groove 15b, the turning press auxiliary member 3 is placed on the auxiliary member base surface 15z which is the upper surface of the portion forming the inner peripheral wall of the seal insertion groove 15b, and the frame auxiliary member seal 11 And the turning press auxiliary member 3 are in a separated state.

  A frame groove 15 x is provided between the frame Oldham groove 15 k in the back pressure chamber 4 and the separation space 300 so as to connect the separation space 300 formed separately and the back pressure chamber 4. The flow path resistance of the frame groove 15x is made to be a shape equal to or lower than the flow path resistance of all the seal holes 11c. The flow path resistance of the pressing portion through hole 3c is also configured to be equal to or less than the flow path resistance of all the seal holes 11c. The pressing portion through hole 3c and the sealing hole 11c are arranged so that the diameters to be installed are different so that the pressing portion through hole 3c and the sealing hole 11c do not overlap. The seal protrusion 11a is an elastic body. The discharge pressure introduced into the auxiliary member back chamber 8 allows the seal protrusion 11a to be pressed against the side surface of the seal insertion groove 15b, and the side surface of the seal insertion groove 15b is sealed, so that the back pressure chamber 4 and the auxiliary member are sealed. The back chamber 8 is shut off.

  It is desirable that the difference between the length of the seal protrusion 11a and the depth of the seal insertion groove 15b be large. Thereby, the separation space 300 is formed to be large, the flow through the separation space 300 described later becomes smooth, and it is possible to avoid poor starting and abnormal increase in back pressure. However, if the difference between the length of the seal projection 11a and the depth of the seal insertion groove 15b is too large, the movement distance of the auxiliary member seal 11 becomes long, and ensuring the wear resistance of the seal projection 11a becomes a problem. Therefore, it is necessary to give an appropriate difference.

  Here, the protruding dimension of the seal projection 11a from the pressing auxiliary plate 3x (seal protrusion length-pressing auxiliary plate thickness) is a force (pressing auxiliary plate) that pushes up the auxiliary member seal 11 more than the frictional force applied thereto. It is necessary to design so as to increase the force applied to the part. Thus, the design is made so that the bulging dimension × the friction coefficient between the seal groove and the seal protrusion <the seal pressing part width than the protruding dimension <the seal pressing part width / the friction coefficient between the seal groove and the seal protrusion. Here, as a material of the seal projection 11a, a plastic or a stainless steel or phosphor bronze metal plate having a spring property can be applied. If the material of the seal pressing portion 11e is the same as the material of the seal protrusion, the auxiliary member seal 11 can be cut out from one material, or injection molding or press molding can be performed.

  Next, operation | movement of the turning press auxiliary | assistant member 3 and the auxiliary member seal | sticker 11 is demonstrated using FIGS. 10-18. Here, in FIG. 10 to FIG. 18, the vertical gaps of the respective members are shown larger than the actual gap dimensions for the sake of explanation.

  The process in which the conforming layer conforms will be described with reference to FIGS. First, the conforming process of the conforming layer provided on the orbiting scroll member 2 will be described. Although FIG. 10 shows a state at the time of assembly, it may be regarded as a state before starting during the familiarization. At this time, the conformable layer 2h1 also remains, and the thickness of the turning end plate 2b is maximum. Although it is necessary to arrange the swivel end plate 2b between the fixed sliding surface 1z and the swivel regulating surface 3a, the swivel pressure assisting member 3 is not applied with back pressure, so that the swivel pressure assisting member 3 is moved downward. Because it escapes, it can be assembled easily. Here, the orbiting scroll member 2 is dimensioned so as to be placed on the orbiting base surface 15 c provided on the frame 15. This is because, if the distance between the fixed sliding surface 2z and the turning sliding surface 2z is excessive, an auxiliary member back pressure or back pressure required to push up the turning pressing auxiliary member 3 toward the fixed scroll member 1 at the time of activation is obtained. This is a gap that requires management. The turning base surface 15c is provided in order to minimize the dimension for determining the gap.

  When starting from the state of FIG. 10, the pressure of the back pressure chamber 4 becomes back pressure and the orbiting scroll member 2 presses against the fixed scroll member 1 as shown in FIG. Further, the pressure in the auxiliary member back chamber 8 becomes the discharge pressure, and the auxiliary member seal 11 is pushed up, and accordingly, the turning pressing auxiliary member 3 is pushed up toward the turning scroll member. Since the protrusion amount H of the protrusion 3b is set to be approximately equal to T, the upper surface of the protrusion 3b is separated from the fixed sliding surface 2z by the thickness of the conformable layer 2h1. As a result, the orbiting scroll member 2 performs the orbiting motion while being sandwiched between the fixed scroll member 1 and the orbiting pressing auxiliary member 3. At this time, in addition to the pressing force due to the back pressure of the back pressure chamber 4 from the fixed scroll member 1 to the orbiting scroll member 2, the pressing force due to the auxiliary member back pressure of the auxiliary member back chamber 8 is also applied. It will sharpen and become familiar. For this reason, the time required for conforming can be shortened, and the reduction of leakage loss due to the shape correction effect of the conforming layer can be achieved in a short time. Furthermore, since the surface of the conforming layer is the conformable layer 2h1, the initial conforming speed becomes very high, and the time required for conforming can be further shortened. The familiar operation is continued until the upper surface of the protrusion 3b presses against the outer peripheral portion of the fixed sliding surface 1z, and the pressing force due to the auxiliary member back pressure of the auxiliary member back chamber 8 applied to the orbiting scroll member 2 decreases.

  FIG. 12 shows a state where the familiar operation is finished. In the normal operation at the end of the familiarization, the pressing force applied to the orbiting scroll member 2 is reduced as compared with the familiarity, so that the mechanical loss is reduced and the performance is improved. Here, depending on the pressing state of the upper surface of the protruding portion 3b and the fixed sliding surface 1z, it becomes possible to continue to apply a part of the auxiliary member back force slightly to the orbiting scroll member 2 even after fitting. In such a state, it is necessary that the turning regulation surface 3a is in contact with the turning back surface 2j. However, by utilizing the elastic deformation of the turning pressing auxiliary member 3 by the auxiliary member seal 11, this state can be set in a wide range of conditions. A state where the surfaces are in contact can be realized. In this case, since an unexpected vibration of the orbiting scroll member 2 can be reduced, an increase in leakage loss and mechanical loss can be suppressed. Further, because of the swirl radiation groove 2x, the pressure in the outer peripheral chamber 7 is almost the same as that in the back pressure chamber 4, and the pressing force can be controlled without considering the sealing property of the swivel regulating surface 3a and the swivel back surface 2j. it can.

  At the end of the familiarization, the thickness of the turning end plate 2b is substantially T, which is substantially equal to the protrusion amount H of the protrusion 3b. This shows that the easy-to-fit layer 2h1 is almost worn out by the dimension setting in which the erosion-precipitation type running layer and T and H are substantially the same. In other words, the familiarity in the familiarization process occupies most of the familiarity of the familiarity layer 2h1, and the familiarity can be easily realized not only in the initial familiarity but also throughout the familiarity. Therefore, since the conforming time can be shortened, the leakage loss due to the conforming layer shape correction effect can be reduced in a short time. In an actual case, the turning end plate 2b thickness T and the protrusion protrusion amount H cannot be made exactly the same due to processing errors. In addition, due to variations in the conforming layer treatment, the sum of the thickness of the conforming difficult layer 2h2 and the base material may deviate from the thickness T of the turning end plate 2b. In the case of H> (summation of familiarity layer 2h2 and the thickness of the base material), the familiarity up to the familiarization end point can be realized by the wear of the easy-to-familiar layer 2h1, so that the familiarization time can be shortened most. it can. On the other hand, when H <(summation of conformance difficult layer 2h2 and the thickness of the base material), the wear progresses to the conformance difficulty layer in the final conformation process. Since the clearance (hereinafter referred to as “rear clearance”) is maintained at substantially 0, the accidental vibration of the orbiting scroll member 2 is suppressed, and an increase in leakage loss and mechanical loss can be suppressed.

  Next, the starting process will be described with reference to FIGS. Here, the case after the familiarization will be described, but the same applies to the activation during the familiarization. Therefore, it also explains the state transition from before startup (FIG. 10) to normal operation (FIG. 11) during assembly or in the middle of familiarization. By the way, there are roughly two cases in the state before activation. This will be described with reference to FIGS. FIG. 13 shows a case where the auxiliary member seal 11 and the turning press auxiliary member 3 are not separated and the seal hole 11c provided in the pressing portion 11b is closed. FIG. 14 shows a case where the auxiliary member seal 11 and the turning press auxiliary member 3 are separated from each other, and a seal hole 11 c provided in the pressing portion 11 b is opened in the separation space 300.

  First, the starting process in the former case shown in FIG. 13 will be described. The fluid is compressed by both scroll members in which the gap substantially the same as the gap determined from the thickness of the turning base surface 15c and the turning end plate 2b is in the axial direction, and the pressurized fluid is compressed by the auxiliary rear discharge pressure introduction passage 15h. Then, the auxiliary member is introduced into the back chamber 8. The projected area of the auxiliary member back chamber 8 is set to an area that can generate a pressing force sufficient to push up the orbiting scroll member 2 even with an insufficient auxiliary member back pressure. As a result, the pressure to the auxiliary member back chamber 8 flows almost simultaneously with the start-up without pressure drop or time delay. When the auxiliary member back chamber 8 is pressurized, the auxiliary member seal 11 rises in the axial direction, and accordingly, the turning pressing auxiliary member 3 is pushed up by the auxiliary member seal 11. Further, the orbiting pressing auxiliary member 3 pushed up by the auxiliary member seal 11 raises the orbiting scroll member 2, and the orbiting scroll member 2 moves to the fixed scroll member 1 side. As a result, the gap between the orbiting scroll member 2 and the fixed scroll member 1 is rapidly reduced, the sealing performance of the compression chamber 200 formed between the orbiting scroll member 2 and the fixed scroll member 1 is improved, and the discharge pressure is increased. Rise to normal pressure. When the discharge pressure rises to a normal pressure, the oil supply to the bearing increases, so that the back pressure is introduced into the back pressure chamber 4 and a pressing force due to this is also generated. Thus, the orbiting scroll member 2 is pressed against the fixed scroll member 1. Thus, since the transitional operation state at the time of startup can be shifted to the normal operation mode in a very short time, a highly reliable scroll fluid machine can be provided.

  Next, the activation process in the latter case shown in FIG. 14 will be described with reference to FIGS. The gap substantially the same as the gap determined from the thickness of the turning base surface 15c and the turning end plate 2b compresses the fluid while the scroll members located in the axial direction are insufficient, and the compressed fluid is supplied to the auxiliary rear discharge pressure introduction passage 15h. It flows into the auxiliary member back chamber 8 via. Since the seal hole 11c opens into the separation space 300, the pressurized fluid that has flowed into the auxiliary member back chamber 8 flows into the separation space 300 through the seal hole 11c, as indicated by the arrows in FIG. Since the seal 3 has substantially the same pressure on the upper and lower surfaces, the seal 3 does not move in the vertical direction, remains in its original position, and the formation of the separation space 300 is continued. Since the separation space 300 communicates with the back pressure chamber 4 mainly through the frame groove 15x and the pressing portion through hole 3c, the pressurized fluid that has entered the separation space 300 flows into the back pressure chamber 4. Therefore, the entire back surface of the orbiting scroll member 2 is almost discharged pressure. As a result, the orbiting scroll member 2 is reliably pressed against the fixed scroll member 1. This is because the upper surface of the swivel end plate 2b is at most a discharge pressure, and there is always a suction pressure region that is lower than the discharge pressure, so that the pressing force generated thereby is less than the pressure generated by the discharge pressure over the entire lower surface. This is because it will always be small. In this way, when the orbiting scroll member 2 is pressed against the fixed scroll member 1, the tooth tip bottom gap of the spiral body, which is the gap in the axial direction of both scroll members, is rapidly reduced and formed between them. The sealing performance of the compression chamber 200 is improved, and the discharge pressure starts to increase toward the normal pressure. Along with this, the pressure in the back pressure chamber 4 also rises, but in the middle, the valve body 100c of the back pressure control valve 100 is pushed up. As a result, as shown in FIG. 15, the pressurized fluid flows out to the suction chamber 6 or the compression chamber 200, and the back pressure, which is the pressure in the back pressure chamber 4, is adjusted to a desired pressure lower than the discharge pressure. By operating the back pressure control valve 100, the pressure in the back pressure chamber 4 is forcibly reduced below the discharge pressure, so that a pressure difference is generated between the auxiliary member back chamber 8 and the back pressure chamber 4, which is the discharge pressure. Arise. Since the seal hole 11c has a flow resistance equal to or higher than that of the frame groove 15x or the pressing portion through hole 3c arranged in series, a pressure difference is generated between the auxiliary member back chamber 8 and the separation space 300. Due to this pressure difference, a force capable of moving the auxiliary member seal 11 upward is generated, and the auxiliary member seal 11 is pressed against the turning pressing auxiliary member 3 as shown in FIG. The auxiliary member seal 11 is pressed against the turning press auxiliary member 3, and the separation space 300 disappears, the seal hole 11 c is closed by the turn pressing auxiliary member 3, and the auxiliary member back chamber 8 and the back pressure chamber by the auxiliary member seal 11 are closed. The seal between 4 is complete. Thereby, the auxiliary member seal 11 is pushed up toward the orbiting scroll member 2 together with the orbiting pressing auxiliary member 3. Therefore, high-efficiency operation with extremely reduced back clearance (clearance between the turning back surface 2j and the turning regulation surface 3a) can be realized.

  Finally, an operation for reducing the back pressure that has risen above the discharge pressure will be described with reference to FIGS. 17 and 18. When the back pressure becomes higher than the discharge pressure, the turning pressing auxiliary member 3 is pushed down, and the auxiliary member seal 11 is lowered accordingly. As shown in FIG. 17, the turning pressing auxiliary member 3 is pushed down to the auxiliary member base surface 15z. After that, as shown in FIG. 18, a back pressure higher than the discharge pressure flows between the swivel pressing auxiliary member 3 and the auxiliary member seal 11 through the pressing portion through hole 3c, and the two are separated from each other. 300 is formed. Thereby, the seal hole 11c is opened, and the back pressure chamber 4 and the auxiliary member back chamber 8 communicate with each other. As a result, a fluid having a pressure higher than the discharge pressure of the back pressure chamber 4 flows into the separation space 300 through the pressing portion through hole 3c and the frame groove 15x, and then enters the auxiliary member back chamber 8 through the seal hole 11c. Finally, it flows out into the internal space of the case 20 that is the discharge pressure through the auxiliary rear discharge pressure introduction passage 15h. This continues until the abnormally increased back pressure drops to the discharge pressure. Thereafter, when the back pressure starts to be lower than the discharge pressure by the control operation of the back pressure control valve 100, the operation is shifted to the normal operation according to the description of FIGS.

  That is, the scroll fluid machine according to the present embodiment is characterized in that the auxiliary member seal 11 includes an opening for communicating the back pressure chamber 4 and the auxiliary member back chamber 8. More specifically, the opening is a seal hole 11 c that penetrates the seal pressing portion 11 e of the auxiliary member seal 11 that presses the turning pressure assisting member 3 from the back pressure chamber 4 toward the turning pressure assisting member 3.

  When the pressure in the back pressure chamber 4 is lower than the discharge pressure, the sealing hole 11c, which is an opening formed in the seal pressing portion 11e, is closed by the turning pressing auxiliary member 3. On the other hand, when the pressure in the back pressure chamber 4 is equal to or higher than the discharge pressure, the turning pressure assisting member 3 is separated from the assisting member seal 11 so that the back pressure chamber 4 and the assisting member back chamber 8 communicate with each other. More specifically, the turning pressure assisting member 3 is separated from the auxiliary member seal 11 by causing the pressure in the back pressure chamber 4 that is equal to or higher than the discharge pressure to flow between the assisting member seal 11 and the turning pressure assisting member 3. Let

  The discharge pressure introduced into the auxiliary member back chamber 8 is introduced into the auxiliary member back chamber 8 from the auxiliary back discharge pressure introduction passage 15h. Here, when the pressure in the back pressure chamber 4 is equal to or higher than the discharge pressure, the pressure in the back pressure chamber 4 passes from the auxiliary rear discharge pressure introduction path 15h through the seal hole 11c until the pressure in the back pressure chamber 4 becomes the discharge pressure. Discharged.

  Although not shown, a preload spring that widens the interval between the seal protrusions 11a can be inserted. Thereby, even when the high-pressure fluid does not flow into the auxiliary member back chamber 8, the seal projection 11a can be pressed against the side surface of the seal insertion groove 15b to secure the seal, so that the start-up can be realized more smoothly. .

  As described above, by providing the auxiliary member seal 11 with the seal hole 11c as an opening, the abnormally increased back pressure can be reduced and quickly adjusted to the appropriate value side. Therefore, damage to the sliding surface due to excessive pressing force of both scroll members can be avoided.

  Further, when there is no seal hole 11c, when the separation space 300 becomes equal to or higher than the discharge pressure, the auxiliary member seal 11 is pressed against the lower surface of the seal insertion groove 15b, and the seal protrusion 11a made of an elastic body is crushed in the vertical direction and damaged. The sealing operation becomes impossible. By providing the means for securing the seal hole and the back space according to the present invention, the auxiliary member seal 11 can be prevented from being pressed against the lower surface of the seal insertion groove 15b, and the reliability of the seal operation can be improved.

  Further, in the case of a differential pressure oil supply type in which oil supply to the bearing is performed by a differential pressure between the back pressure and the discharge pressure, oil supply to the bearing is not performed if the back pressure rises above the discharge pressure. However, according to the present embodiment, it is possible to quickly avoid a state in which oil supply to the bearing is not performed, so that damage to the bearing can be prevented, and a highly reliable fluid machine can be provided. More specifically, even if the back pressure is reduced to the discharge pressure, the differential pressure oil supply does not operate. However, the oil supply in this embodiment is applied to the oil supply hole 9b formed in the center of the crankshaft 9 and the outer periphery of the crankshaft 9. Since centrifugal lubrication due to a diameter difference at a certain lubrication hole outlet is also provided, if the back pressure can be reduced to the discharge pressure, lubrication by centrifugal lubrication is performed, so that damage to the bearing can be avoided.

  A second embodiment of the scroll fluid machine according to the present invention will be described with reference to FIG. FIG. 19 is an enlarged longitudinal sectional view in the vicinity of the back space. When the back pressure is equal to or higher than the discharge pressure, the opening of the pressing portion through hole 3c is connected on the back side of the turning pressure assisting member 3 as a seal separating means for separating the auxiliary member seal 11 and the turning pressure assisting member 3 from each other. A pressure introducing groove 3d is provided. Since the configuration other than the pressure introducing groove 3d is the same as that of the first embodiment, its detailed description is omitted.

  The pressure introducing groove 3d is provided at a position not over the seal hole 11c. When the back pressure is equal to or higher than the discharge pressure, the auxiliary member seal 11 is not pressed against the turning press auxiliary member 3. Here, since oil is contained between the auxiliary member seal 11 and the turning press auxiliary member 3, a situation in which a high-pressure back pressure fluid is difficult to enter between the auxiliary member seal 11 and the turn pressing auxiliary member 3 occurs. However, a wide back pressure region is always ensured between the turning pressing auxiliary member 3 and the auxiliary member seal 11 by the pressure introducing groove 3d. For this reason, when the back pressure becomes equal to or higher than the discharge pressure, the auxiliary member seal 11 is pushed downward and deformed by the pressure in the back pressure region, and the swivel pressing auxiliary member 3 and the auxiliary member around the pressure introducing groove 3d are deformed. A gap is created between the seals 11. When this happens, back pressure is also applied to this gap, so the back pressure region is expanded. In this back pressure region, the deformation of the auxiliary member seal 11 increases as the back pressure region increases, and as a result, a large gap is generated, and the expansion speed increases. Therefore, by providing the pressure introducing groove 3d, when the back pressure becomes equal to or higher than the discharge pressure, the separating operation of the turning pressing auxiliary member 3 and the auxiliary member seal 11 can be completed in a short time. As a result, the abnormal back pressure above the discharge pressure can be reduced in a short time, and the sliding surfaces of the scroll members, the auxiliary member seals, and the reliability of the bearing can be further improved.

  In the present embodiment, the groove that connects the opening of the pressing portion through hole 3c is provided. However, the present invention is not limited to this, and may have a digging shape that digs around the opening of the pressing portion through hole 3c. In this case, it is possible to suppress a decrease in the rigidity of the turning press assisting member 3 and to facilitate dimension management of the turning press assisting member. In addition, if a groove connecting the opening of the pressing portion through hole 3c is provided on the auxiliary member seal 11 side, it is possible to avoid a decrease in the rigidity of the rotating press auxiliary member 3, so that the size control of the rotating press auxiliary member becomes easier. .

  A third embodiment of the scroll fluid machine according to the present invention will be described with reference to FIG. FIG. 20 is an enlarged longitudinal sectional view in the vicinity of the back space. As the seal separating means, an auxiliary member seal, a turning pressing auxiliary member, and a compressed elastic body are arranged. Specifically, a plate-like separation spring 12 that is a wave plate spring is provided in the pressure introduction groove 3d. Since the configuration other than the plate-like separation spring 12 is the same as that of the second embodiment, its detailed description is omitted.

  Since the compressed plate-like separation spring 12 is arranged in the pressure introducing groove 3d, when the back pressure is equal to or higher than the discharge pressure, the action of separating the turning pressing auxiliary member 3 and the auxiliary member seal 11 by the force of the plate-like separation spring 12 is triggered. Can be generated. Thereby, back pressure can be smoothly introduced from the pressing part through hole 3c and the frame groove 15x, and the separation space 300 can be formed quickly. As a result, the abnormal back pressure above the discharge pressure can be further reduced in a short time, and the sliding surfaces of both scroll members, auxiliary member seals and bearings can be further improved in reliability.

  If the pressing part through-hole 3c is arrange | positioned in the peak part of the plate-shaped separation spring 12, it will block an opening part. For this reason, the number of the pressing part through-holes 3c and the number of the peaks of the plate-like separation spring 12 are made prime. The crests of the pressing portion through hole 3c and the plate-like separation spring 12 are formed at equal intervals. As a result, even in the worst case, only one seal hole and one pressing portion through-hole need to be closed, so there is no problem in the flow of fluid through both holes. Moreover, while arrange | positioning the press part through-hole 3c in the intermediate position of the two peaks of the plate-shaped separation spring 12, and fixing only one place of the peaks of the plate-shaped separation spring 12 in the pressure introduction groove 3d, You may prescribe | regulate the rotational positional relationship of the plate-shaped separation spring 12 and the press part through-hole 3c. And let the number of the press part through-holes 3c be the same number as the number of hills, or a multiple. Thereby, since the number of the press part through-holes 3c to open becomes constant, starting and back pressure raise avoidance performance are stabilized.

  In the present embodiment, the plate-like separation spring 12 is housed in the groove provided on the turning pressing auxiliary member, but the housing groove may be provided on the auxiliary member seal 11 side (see the groove drawn with a dotted line). Further, the plate-like separation spring 12 may be simply sandwiched between the turning pressing auxiliary member 3 and the auxiliary member seal 11. In this case, the plate-like separation spring 12 needs to be flat when the turning pressing auxiliary member 3 and the auxiliary member seal 11 are pressed, and the spring strength is set to the minimum while ensuring the separation operation.

  A fourth embodiment of the scroll fluid machine according to the present invention will be described with reference to FIG. FIG. 21 is an enlarged longitudinal sectional view of the vicinity of the back space. As a seal separation means, a helical separation spring 13 which is a helical spring is provided between the turning pressing auxiliary member 3 and the auxiliary member seal 11. Since the configuration other than the helical separation spring 13 is the same as that of the second embodiment, a detailed description thereof will be omitted.

  Since the helical spring 13 is disposed below the pressing portion through hole 3c, no problem occurs as described in the second embodiment, and the openings of the seal hole 11c and the pressing portion through hole 3c are always secured. Thereby, since the same seal hole 11c and the pressing part through-hole 3c can always operate as a fluid flow path, the escape operation of the high-pressure fluid from the back pressure chamber 4 can be stabilized.

  A fifth embodiment of the scroll fluid machine according to the present invention will be described with reference to FIG. FIG. 22 is an enlarged longitudinal sectional view in the vicinity of the back space. Let the seal | sticker press part 11e of the auxiliary member seal | sticker 11 be the auxiliary | assistant member seal | sticker 11 which has the dome-shaped seal | sticker press part 11e1 which raised the dome shape. Since the configuration other than the auxiliary member seal 11 having the dome-shaped seal pressing portion 11e1 is the same as that of the first embodiment, its detailed description is omitted.

  Since the dome-shaped seal pressing portion 11e1 has a spring action, it can be regarded as a seal separating means. Therefore, since the seal and the seal separating means are integrated, the number of parts can be reduced. In FIG. 22, for the sake of explanation, the curvature of the dome-shaped seal pressing portion is shown with emphasis, but in actuality, the amount of protrusion by the protrusion is set to about 0.05 to 1 mm.

  A sixth embodiment of the scroll fluid machine according to the present invention will be described with reference to FIG. FIG. 23 is an enlarged vertical sectional view of the vicinity of the back space. Instead of the swivel base groove, the upper surface of the swivel pressure auxiliary member 3 placed on the auxiliary member base surface 15z is used, and in order to connect the outer peripheral chamber 7 to the back pressure chamber 4, a swirl pressure auxiliary member is used instead of the swirl radiation groove. 3 is provided with an inclined hole 3f. Since the configuration other than the above is the same as that of the fifth embodiment, detailed description thereof is omitted.

  By making the upper surface of the turning press auxiliary member 3 the turning base surface, the space for providing the turning base surface becomes unnecessary, and the pressing auxiliary plate portion 3x expands. Therefore, since it becomes possible to sufficiently secure the area facing the orbiting scroll member even in a place where the orbiting scroll member is narrowed by the orbiting motion, excessive pressing force is not applied even when the pressing auxiliary plate portion 3x presses against the orbiting scroll member. Both damages can be avoided.

  Moreover, since the radial groove on the outer peripheral side of the orbiting scroll member 2 can be eliminated by providing the inclined hole 3f, the rigidity of the orbiting end plate 2b can be increased, and deformation due to load or heat can be reduced. Therefore, since the gap between the scroll members can be easily managed, leakage can be suppressed, and as a result, a higher-performance scroll fluid machine can be provided.

  Further, in the present embodiment, in order to provide a plurality of inclined holes 3f, circular grooves of an inlet groove 3g and an outlet groove 3e that connect these both ends are provided. Further, an annular protrusion 11f is provided at the center of the lower surface of the seal pressing portion 11e of the auxiliary member seal 11. As a result, the rigidity of the auxiliary member seal 11 is increased, and damage to the seal pressing portion 11e that is pressed to exhibit the sealing performance is reduced, so that the reliability can be improved.

The longitudinal cross-sectional view of the scroll fluid machine in 1st Example. The rear view of the fixed scroll member in 1st Example. The longitudinal cross-sectional view of the turning scroll member in 1st Example. The rear view of the turning scroll member in 1st Example. The top view of the flame | frame in 1st Example. The longitudinal cross-sectional view of the turning press auxiliary | assistant member in 1st Example. The top view of the turning press auxiliary | assistant member in 1st Example. The top view of the auxiliary member seal | sticker in 1st Example. The longitudinal cross-sectional view of the auxiliary member seal | sticker in 1st Example. The expanded longitudinal cross-sectional view of the turning press auxiliary | assistant member in 1st Example (at the time of an assembly or before familiarity & before starting). The expanded longitudinal cross-sectional view (during a familiar operation) of the turning press auxiliary | assistant member in 1st Example. The expanded longitudinal cross-sectional view of the turning press auxiliary member in 1st Example (after familiarity & normal operation). The expanded longitudinal cross-sectional view of the turning press auxiliary | assistant member in 1st Example (Before starting in case there is no back space before starting). The expanded longitudinal cross-sectional view of the turning press auxiliary | assistance member in 1st Example (just after starting in case there exists back space before starting). The expanded longitudinal cross-sectional view of the turning press auxiliary member in 1st Example (after back pressure pressurization in case there exists back space before starting). The expanded longitudinal cross-sectional view of the turning press auxiliary | assistant member in 1st Example (after auxiliary member seal raises in case there exists back space before starting). The expanded longitudinal cross-sectional view of the turning press auxiliary member in 1st Example (immediately after the back space formation start when a back pressure becomes more than discharge pressure). The expanded longitudinal cross-sectional view of the rotation press auxiliary member in 1st Example (The state which the rotation press auxiliary member and auxiliary member seal | sticker fall when a back pressure becomes more than discharge pressure, and is reducing the back pressure). The expansion longitudinal cross-sectional view of back surface space vicinity in 2nd Example. The expansion longitudinal cross-sectional view of back surface space vicinity in 3rd Example. The expansion longitudinal cross-sectional view of back surface space vicinity in 4th Example. The expanded longitudinal cross-sectional view of back surface space vicinity in 5th Example. The expanded longitudinal cross-sectional view of back space vicinity in 6th Example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Fixed scroll member 1a Fixed spiral body 1b Fixed end plate 2 Orbiting scroll member 2a Orbiting spiral member 2b Orbiting end plate 2c Orbiting bearing 2x Orbiting radiation groove 3 Orbiting pressing auxiliary member 3b Protruding portion 3c Pressing portion through hole 3d Pressure introducing groove 3x Pressing Auxiliary plate portion 4 Back pressure chamber 5 Oil storage chamber 6 Suction chamber 7 Outer chamber 8 Auxiliary member back chamber 9 Crankshaft 9a Eccentric pin 9b Oiling hole 10 Oiling pipe 11 Auxiliary member seal 11a Seal projection 11c Seal hole 11e Seal pressing portion 11e1 Dome Mold seal pressing portion 12 Plate-like separation spring 13 Spiral-like separation spring 15 Frame 15a Main bearing 15b Seal insertion groove 15h Auxiliary rear discharge pressure introduction path 15x Frame groove 15z Auxiliary member base surface 16 Oldham ring 17 Motor 18 Suction pipe 19 Discharge pipe 20 Case 100 Back pressure control valve 200 Compression chamber 300 Spacing space

Claims (11)

A fixed scroll member, a orbiting scroll member that forms a compression chamber in cooperation with the fixed scroll member, a back pressure chamber provided on the back side of the orbiting scroll member, and the orbiting scroll member to the fixed scroll member Back pressure control means for controlling the pressure of the back pressure chamber so as to press, a turning pressure auxiliary member that is provided opposite to the back surface of the orbiting scroll member and is movable in the axial direction, and the turning pressure auxiliary member The auxiliary member back chamber, which is located on the opposite side of the orbiting scroll member and into which discharge pressure is introduced, and the auxiliary member back chamber and the back pressure chamber are shut off, and are movable in the axial direction to move in the auxiliary member back chamber. In a scroll fluid machine comprising: an auxiliary member seal that presses the orbiting scroll auxiliary member toward the orbiting scroll member by discharge pressure;
The scroll fluid machine according to claim 1, wherein the auxiliary member seal has an opening configured to communicate the back pressure chamber and the auxiliary member back chamber. The said opening part is a seal hole which penetrates the seal | sticker press part of the said auxiliary member seal which presses the said rotation press auxiliary member from the said back pressure chamber toward the said auxiliary member back chamber. The scroll fluid machine as described.   When the pressure in the back pressure chamber is lower than the discharge pressure, the opening is closed by the turning pressure assisting member, and when the pressure in the back pressure chamber is equal to or higher than the discharge pressure, the turning pressure assisting member is connected to the auxiliary member seal. The scroll fluid machine according to claim 1 or 2, wherein the back pressure chamber and the auxiliary member back chamber communicate with each other by being separated from each other.   The turning pressure assisting member is separated from the auxiliary member seal by causing the pressure in the back pressure chamber, which is equal to or higher than the discharge pressure, to flow between the auxiliary member seal and the turning pressure assisting member. The scroll fluid machine according to claim 3. The discharge pressure introduced into the auxiliary member back chamber is introduced from the auxiliary back discharge pressure introduction path into the auxiliary member back chamber,
When the pressure in the back pressure chamber is equal to or higher than the discharge pressure, the pressure in the back pressure chamber is discharged from the auxiliary back surface discharge pressure introduction path through the opening until the pressure in the back pressure chamber becomes the discharge pressure. The scroll fluid machine according to claim 3 or 4, characterized in that.   The scroll according to any one of claims 1 to 5, further comprising seal separating means for separating the auxiliary member seal and the turning pressing auxiliary member when the pressure in the back pressure chamber is equal to or higher than the discharge pressure. Fluid machinery. The seal separating means applies the pressure of the back pressure chamber, which is equal to or higher than the discharge pressure, to the swivel pressure auxiliary member side of the auxiliary member seal on the surface of the back pressure chamber and the swivel pressure auxiliary member side of the auxiliary member seal. The scroll fluid machine according to claim 6, further comprising a back pressure introduction path that is connected and introduced. The back pressure introduction path includes a dug portion provided at a position not on the seal hole on the auxiliary member seal side of the orbiting press auxiliary member, the dug portion and the orbiting scroll member side of the orbiting press auxiliary member, The scroll fluid machine according to claim 7, wherein the scroll fluid machine comprises a pressing portion through hole that connects the two. The scroll fluid machine according to claim 7 or 8, wherein a compressed elastic body is disposed between the auxiliary member seal and the turning pressing auxiliary member. The auxiliary member seals said by Moriagara the seal pressing portion center of the auxiliary member sealing a dome shape, a scroll fluid machine according to claim 7 or 8, characterized in that have a domed seal pressing portion. 11. The scroll fluid machine according to claim 1, wherein a height of the auxiliary member seal is lower than a height of a seal insertion groove into which the auxiliary member seal is inserted.

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