JP2011236999A - Bearing structure of rotary machine, revolving speed control device, and refrigerating cycle control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bearing structure for rotatably supporting a rotating shaft of a rotary machine and a revolving speed control device for controlling a revolving speed of the rotary machine applying the bearing structure, and to improve reliability of the bearing structure concerning a refrigerating cycle control device for controlling operation of a refrigerating cycle provided with a compressor applying the bearing structure.SOLUTION: The bearing structure is provided with a rotating regulation means 263 for fixing a sliding bearing 261 rotatably supporting a shaft 25 on an inside race 262a of a rolling bearing 262 and regulating relative rotation of the inside race 262a and the outside race 262b of the rolling bearing 262 until rotating torque transmitted from the sliding bearing 261 to the rolling bearing 262 is a preset reference rotating torque or above. Thereby the shaft 25 is supported by the sliding bearing 261 with high reliability rather than the rolling bearing 262 until the rotating torque is the reference rotating torque or more. Furthermore, when the rotating torque is the reference rotating torque or above, the relative rotation of the inside race 262a and the outside race 262b is allowed to support the shaft 25 with the rolling bearing 262 so as to suppress wear of the sliding bearing 261.

Description

  The present invention relates to a bearing structure that rotatably supports a rotating shaft of a rotary machine, a rotational speed control device that controls the rotational speed of the rotary machine to which the bearing structure is applied, and a compressor to which the bearing structure is applied. The present invention relates to a refrigeration cycle control device that controls the operation of a refrigeration cycle.

  Conventionally, a sliding bearing and a rolling bearing are known as bearings that rotatably support a rotating shaft of a rotating machine including rotating parts such as a compression mechanism, a blower mechanism, an electric motor, and a generator.

  For example, a sliding bearing is formed of a substantially cylindrical member, and its outer peripheral surface is fixed to a fixing member such as a housing, and its inner peripheral surface (bearing surface) supports the outer peripheral surface of the rotating shaft. Are known. In addition, as a rolling bearing, a rolling element is interposed between an inner annular member connected to a rotating shaft of a rotating machine and an outer annular member fixed to a fixed member, and the inner annular member and the outer annular member are relatively rotated. What is to be known is known.

  By the way, in general, a sliding bearing is often used as a bearing for a rotary machine in which the rotational speed of the rotary shaft is relatively high and the rotational speed can vary, such as the compression mechanism described above. The reason is that the sliding bearing has a lower number of components and a lower cost than a rolling bearing and can be expected to have high reliability (long life).

  More specifically, in a rolling bearing, since the rolling element is constantly rotating while contacting the inner annular member and the outer annular member while the rotating shaft of the rotating machine is rotating, the rolling element may be worn. There is. On the other hand, in a sliding bearing, a lubricant such as oil is supplied between the bearing surface and the outer peripheral surface of the rotary shaft to form an oil film so that the bearing surface and the outer peripheral surface of the rotary shaft are worn. High reliability can be expected with suppression.

  Further, Patent Document 1 employs a sliding bearing as a bearing for a rotary machine, and at least one of a bearing surface of the sliding bearing and an outer peripheral surface of the rotating shaft that is in sliding contact with the bearing surface is mainly made of fluororesin and polyimide resin. A bearing structure for a rotary machine is disclosed that aims to suppress wear on the bearing surface and the outer peripheral surface of the rotating shaft, compared with the case where a relatively hard film containing graphite is formed by forming a resin film as a component. Yes.

JP 2006-16992 A

  However, according to the study by the present inventors, when the bearing structure of Patent Document 1 is applied to a rotating machine that repeatedly operates and stops, the resin film is worn and the reliability improvement effect by adopting the sliding bearing May not be sufficiently obtained.

  The reason is that if the rotating machine is left in a stopped state, the oil film formed between the bearing surface of the sliding bearing and the outer peripheral surface of the rotating shaft will break, and the bearing surface will This is because a boundary lubrication state in which the oil film is cut between the outer peripheral surface of the rotating shaft and the outer peripheral surface of the rotating shaft is obtained. When such boundary lubrication is repeated, the resin film softer than metal or the like is easily worn, and the effect of improving the reliability by adopting the sliding bearing cannot be obtained sufficiently.

  In view of the above points, an object of the present invention is to improve the reliability of a bearing structure of a rotary machine.

  Another object of the present invention is to provide a rotational speed control device for a rotary machine that can improve the reliability of the bearing structure of the rotary machine.

  Another object of the present invention is to provide a refrigeration cycle control device capable of improving the reliability of a bearing structure applied to a compressor of a refrigeration cycle.

The present invention has been devised to achieve the above object. In the invention according to claim 1, a sliding bearing (261) that rotatably supports a rotating shaft (25) of a rotating machine (20), and A rolling bearing (262) for rotating the inner annular member (262a) and the outer annular member (262b) relative to each other with a rolling element (262c) interposed between the inner annular member (262a) and the outer annular member (262b). The sliding bearing (261) is fixed to the inner annular member (262a),
Furthermore, the inner annular member (262a) and the outer annular member (262b) rotate relative to each other until the rotational torque transmitted from the sliding bearing (261) to the rolling bearing (262) becomes equal to or higher than a predetermined reference rotational torque. It is characterized by a bearing structure of a rotary machine provided with a rotation restricting means (263) for restricting the end of the rotation.

  According to this, since the rotation restricting means (263) is provided, the rolling bearing (262) until the rotational torque transmitted from the sliding bearing (261) to the rolling bearing (262) becomes equal to or higher than the reference rotational torque. The rotating shaft (25) can be supported by the sliding bearing (261) having higher reliability.

  On the other hand, when the rotational torque becomes equal to or higher than the reference rotational torque, the inner annular member (262a) and the outer annular member (262b) can be rotated relative to each other, so that the rotating shaft (25) is rotated by the rolling bearing (262). Can be supported.

  Accordingly, the friction between the bearing surface of the sliding bearing (261) and the outer peripheral surface of the rotating shaft (25) is the same as when the rotational torque received by the rolling bearing (262) from the sliding bearing (261) becomes equal to or higher than the reference rotational torque. Under an operating condition in which the force increases, the rotating shaft can be supported by the rolling bearing (262) without sliding the bearing surface of the sliding bearing (261) and the outer peripheral surface of the rotating shaft (25).

  Thereby, it can suppress that a slide bearing (261) wears, and can improve the reliability of the bearing structure of a rotary machine.

  In the invention according to claim 2, in the bearing structure of the rotary machine according to claim 1, the rotation amount detecting means (264) for detecting the relative rotation amount between the inner annular member (262a) and the outer annular member (262b). ). According to this, the rotational torque received by the rolling bearing (262) from the sliding bearing (261) can be detected based on the detected relative rotation amount between the inner annular member (262a) and the outer annular member (262b).

  Further, as in the invention according to claim 3, specifically, in the bearing structure of the rotary machine according to claim 2, the rotation restricting means (263) is fixed to the outer annular member (262b) side to rotate torque. And a plate-like elastic member (263b) that is elastically deformed with an increase in the number of holes, and an abutting member (263a) that is fixed to the inner annular member (262a) and contacts the elastic member (263b). The elastic member (263b) may be configured to contact the contact member (263a) until the rotational torque becomes equal to or higher than the reference rotational torque.

  According to this, since the elastic member (263b) contacts the contact member (263a) until the rotational torque becomes equal to or higher than the reference rotational torque, the inner annular member (262a) and the outer annular member (262b) rotate relative to each other. Can be regulated. On the other hand, when the rotational torque becomes equal to or greater than the reference rotational torque and the elastic member (263b) is elastically deformed until it cannot contact the contact member (263a), the inner annular member (262a) and the outer annular member (262b) Relative rotation is possible.

  In addition, after the rotational torque increases to the reference rotational torque or more, when the rotational torque becomes smaller than the reference rotational torque again, the elastic member (263b) returns to the shape of contacting the contact member (263a), so that the inner annular shape is again formed. The relative rotation of the member (262a) and the outer annular member (262b) can be restricted.

  Note that “fixed to the outer annular member (262b)” in this claim does not mean that the outer annular member (262b) itself is fixed, but the outer annular member (262b). In contrast, this means includes a member that does not relatively change its position, for example, a fixing member to which the outer annular member (262b) is fixed.

  In addition, the expression “fixed to the inner annular member (262a)” in this claim does not mean that the inner annular member (262a) itself is fixed, but the inner annular member (262a). It is meant to include a member that does not relatively change its position, for example, a plain bearing (261) fixed to the inner annular member (262a).

  Further, as in the invention according to claim 4, specifically, in the bearing structure of the rotary machine according to claim 3, the rotation amount detection means is a strain gauge (264) that detects the strain amount of the elastic member (263 b). ). Thereby, the rotation amount detection means (264) can be easily configured.

  Further, as in the invention according to claim 5, specifically, in the bearing structure of the rotary machine according to claim 1, the rotation restricting means (263) includes the outer annular member (262b) side and the inner annular member (262a). ) Side, and the connecting member (263e) may be formed so as to break when the rotational torque becomes equal to or higher than the reference rotational torque. According to this, the rotation restricting means can be realized with an extremely simple configuration.

  According to a sixth aspect of the present invention, there is provided a rotational speed control device for controlling the rotational speed of the rotary shaft (25) of the rotary machine (20) to which the rotary machine bearing structure according to the second aspect is applied. The present invention is characterized by a rotation speed control device that reduces the rotation speed of the rotation shaft (25) when the relative rotation amount detected by the amount detection means (264) becomes equal to or greater than a predetermined reference relative rotation amount.

  According to this, when the relative rotation amount detected by the rotation amount detection means (264) becomes equal to or greater than a predetermined reference relative rotation amount, the rotational speed of the rotary shaft (25) is reduced, so that the rolling bearing ( 262) can reduce the rotational torque received from the sliding bearing (261). Therefore, the rotating shaft (25) can be supported by the sliding bearing (261) having higher reliability than the rolling bearing (262).

  Furthermore, even if the rotational torque does not decrease even if the rotational speed of the rotating shaft (25) is reduced, the inner annular member (262a) is applied because the bearing structure for a rotary machine described in claim 2 is applied. ) And the outer annular member (262b) rotate relative to each other, and the rotating shaft (25) can be supported by the rolling bearing (262). Thereby, it can suppress that a slide bearing (261) wears.

  Therefore, it is possible to provide a rotational speed control device for a rotary machine that can improve the reliability of the bearing structure of the rotary machine.

  The invention according to claim 7 is a refrigeration cycle (1) comprising a compression mechanism (20) to which the bearing structure of the rotary machine according to claim 2 is applied, and a variable throttle mechanism (12) for decompressing and expanding high-pressure refrigerant. ) Of the variable throttle mechanism (12) when the relative rotation amount detected by the rotation amount detection means (264) is equal to or greater than a predetermined reference relative rotation amount. It features a refrigeration cycle control device that increases the throttle opening.

  According to this, when the relative rotation amount detected by the rotation amount detection means (264) becomes equal to or larger than a predetermined reference relative rotation amount, the throttle opening degree of the variable throttle mechanism (12) is increased. By reducing the pressure difference between the suction side pressure and the discharge side pressure of the compression mechanism (20), which is a machine, the frictional force between the bearing surface of the sliding bearing (261) and the outer peripheral surface of the rotary shaft (25) can be reduced. it can.

  Therefore, the rotational torque that the rolling bearing (262) receives from the sliding bearing (261) can be reduced, and the rotating shaft (25) is supported by the sliding bearing (261) that is more reliable than the rolling bearing (262). Can do.

  Further, even when the throttle opening degree of the variable throttle mechanism (12) is increased, even if the rotational torque does not decrease, the bearing structure for the rotary machine according to claim 2 is applied, so the inner annular member (262a). And the outer annular member (262b) rotate relative to each other, and the rotating shaft (25) can be supported by the rolling bearing (262). Thereby, it can suppress that a slide bearing (261) wears.

  Therefore, it is possible to provide a refrigeration cycle control device that can improve the reliability of the bearing structure applied to the compressor of the refrigeration cycle.

  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 an axial sectional view of the compressor of a 1st embodiment. It is AA sectional drawing of FIG. It is the B section enlarged view of FIG. It is an axial sectional view of the compressor of the second embodiment. It is an axial direction sectional view of the compressor of a 3rd embodiment. It is CC sectional drawing of FIG. It is the D section enlarged view of FIG. (A) is a time chart which shows the change of the rotation speed of a compressor at the time of compressor starting, and the change of relative rotation amount, (b) is the throttle opening degree and relative rotation of an electric expansion valve at the time of compressor start-up. It is a time chart which shows the change of quantity. (A) is a time chart which shows the rotation speed change of the compressor at the time of a compressor stop of a prior art, and the change of relative rotation amount, (b) is an electric expansion valve at the time of the compressor starting of this embodiment It is a time chart which shows the opening degree of this, the rotation speed change of a compressor, and the change of relative rotation amount.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a schematic axial sectional view of a compressor 10 including a compression mechanism 20 that is a rotary machine of the present embodiment. The compressor 10 is applied to a heat pump cycle (vapor compression refrigeration cycle) 1 and compresses and discharges a refrigerant.

  In addition, the up and down arrows in FIG. 1 indicate the up and down directions when the compressor 10 is mounted on the heat pump cycle 1. Further, in FIG. 1, the connection relationship between the constituent devices constituting the compressor 10 and the heat pump cycle 1 is also schematically illustrated.

  The heat pump cycle 1 of the present embodiment is applied to a heat pump type hot water heater that heats hot water by moving the amount of heat absorbed from outside air to the hot water, and as shown in FIG. The refrigerant heat exchanger 11, the electric expansion valve 12, and the outdoor evaporator 13 are connected in a ring shape.

  The water-refrigerant heat exchanger 11 is a heating heat exchanger that heats hot water by exchanging heat between the refrigerant discharged from the compressor 10 and hot water. The electric expansion valve 12 is a decompression means for decompressing and expanding the refrigerant flowing out of the water-refrigerant heat exchanger 11. The outdoor evaporator 13 is an endothermic heat exchanger that evaporates by exchanging heat of the refrigerant decompressed and expanded by the electric expansion valve 12 with the outside air.

  More specifically, the electric expansion valve 12 includes a valve body configured to be able to change the throttle opening and an electric actuator including a stepping motor that changes the throttle opening of the valve body. This is a variable aperture mechanism. The operation of the electric actuator is controlled by a control signal output from a refrigeration cycle control device 60 described later.

  Furthermore, in the heat pump cycle 1 of the present embodiment, carbon dioxide is employed as the refrigerant, and a supercritical refrigeration cycle in which the high-pressure refrigerant discharged from the compressor 10 is equal to or higher than the critical pressure of the refrigerant is configured. The refrigerant is mixed with oil (refrigeration oil) that lubricates each sliding portion inside the compressor 10, and a part of this oil circulates in the cycle together with the refrigerant.

  Next, the detailed structure of the compressor 10 of this embodiment is demonstrated. The compressor 10 according to this embodiment includes a scroll-type compression mechanism 20, an electric motor 30 as a driving unit that drives the compression mechanism 20, and the like accommodated in a housing 40 that forms an outer shell of the compressor 10. Machine. The rotation speed (refrigerant discharge capacity) of the compressor 10 (specifically, the electric motor 30) is controlled by a control signal output from the refrigeration cycle control device 60.

  Further, as shown in FIG. 1, the compressor 10 has a rotating shaft of a shaft 25 that constitutes a rotating shaft of the compression mechanism 20 extending in the vertical direction (vertical direction), so that the compression mechanism 20 and the electric motor 30 are connected in the vertical direction. It is configured in the so-called vertical installation type. More specifically, in the present embodiment, the compression mechanism 20 is disposed below the electric motor 30.

  The housing 40 has a cylindrical member 41 extending in the vertical direction, an upper lid member 42 that closes the upper end portion of the cylindrical member 41, and a lower lid member 43 that closes the lower end portion of the cylindrical member 41, and these are joined together by welding. Thus, a sealed container structure is obtained. Therefore, the housing 40 is formed in a vertically long shape extending in the vertical direction.

  The electric motor 30 includes a stator 31 that forms a stator and a rotor 32 that forms a rotor. The stator 31 includes a stator core 31a made of a magnetic material and a stator coil 31b wound around the stator core 31a. When electric power is supplied to the stator coil 31b via a power supply terminal (not shown), a rotating magnetic field that rotates the rotor 32 is generated.

  The rotor 32 is formed in a substantially cylindrical shape extending in the rotation axis direction, and is disposed on the inner peripheral side of the stator 31. Further, the rotor 32 is configured to have a permanent magnet, and a shaft 25 that is a rotating shaft of the compression mechanism 20 is fixed by press-fitting into a through hole provided at the center thereof. Therefore, when electric power is supplied to the stator coil 31b and a rotating magnetic field is generated, the rotor 32 and the shaft 25 rotate together.

  The shaft 25 is formed to have a longer length in the rotational axis direction than the rotor 32, and can be rotated by the first bearing portion 26 at a portion below the lowermost end portion of the rotor 32 (on the compression mechanism 20 side). The second bearing portion 27 is rotatably supported at a portion above the uppermost end portion of the rotor 32 (on the opposite side of the compression mechanism 20).

  More specifically, a flange portion 25a that extends in the horizontal direction perpendicular to the rotation axis direction is formed at a lower portion of the shaft 25 than the rotor 32, and is lower than the rotor 32 of the shaft 25. Of the parts, a part between the rotor 32 and the flange part 25 a is rotatably supported by a first bearing part 26 fixed to the middle housing 44. The detailed configuration of the first and second bearing portions 26 and 27 will be described later.

  The middle housing 44 functions as a fixing member to which the first bearing portion 26 and the like are fixed, and the outer peripheral side thereof is fixed to the inner peripheral surface of the tubular member 41 of the housing 40. Further, in the shaft 25, an eccentric portion 25 b that is eccentric with respect to the rotation center of the shaft 25 is formed at the lower end portion on the lower side of the flange portion 25 a.

  Further, inside the shaft 25 of the present embodiment, the main oil supply passage 25c through which the above-described lubricating oil flows, and the main oil supply passage 25c to the sliding portion between the outer peripheral surface of the shaft 25 and the first bearing portion 26. A first sub oil supply passage 25d that guides oil and a second sub oil supply passage 25e that guides oil from the main oil supply passage 25c to the sliding portion between the outer peripheral surface of the shaft 25 and the second bearing portion 27 are formed.

  The scroll-type compression mechanism 20 includes a movable scroll 21 that revolves as the shaft 25 rotates, and a fixed scroll 22 that forms a working chamber 23 that compresses the refrigerant together with the movable scroll 21.

  More specifically, the fixed scroll 22 includes a disk-shaped substrate portion 22a and a spiral tooth portion 22b protruding from the substrate portion 22a toward the movable scroll 21 side. Further, the outer peripheral side of the substrate portion 22 a of the fixed scroll 22 is fixed to the inner peripheral surface of the cylindrical member 41 of the housing 40.

  On the other hand, the movable scroll 21 has a disk-shaped substrate portion 21a and a spiral tooth portion 21b that protrudes from the substrate portion 21a toward the fixed scroll 22 side and meshes with the tooth portion 22b of the fixed scroll 22. Has been. In addition, an eccentric portion 25b formed at the lower end portion of the shaft 25 is inserted into a central portion of the upper surface side (the side opposite to the side where the tooth portion 21b is provided) of the substrate portion 21a of the movable scroll 21. A boss portion 21c is formed.

  Further, between the movable scroll 21 and the middle housing 44, a rotation prevention mechanism (not shown) that prevents the movable scroll 21 from rotating around the eccentric portion 25b is provided. For this reason, when the shaft 25 rotates, the movable scroll 21 revolves while turning around the rotation center of the shaft 25 without rotating around the eccentric portion 25b.

  The tooth portions 21b and 22b of the scrolls 21 and 22 are engaged with each other and contacted at a plurality of locations, thereby forming a plurality of working chambers 23 formed in a crescent shape when viewed from the rotation axis direction. In FIG. 1, for clarity of illustration, only one working chamber among the plurality of working chambers 23 is denoted by reference numerals, and the other working chambers are not denoted by reference numerals.

  The working chamber 23 moves while reducing the volume from the outer peripheral side to the center side in the circumferential direction of the rotation axis by the revolving motion of the movable scroll 21. Thereby, the refrigerant in the working chamber 23 is compressed. Furthermore, the working chamber 23 formed on the outermost peripheral side of the tooth portions 21b and 22b of the scrolls 11 and 12 is supplied with a refrigerant through a refrigerant supply passage 23a communicating with the outlet side of the outdoor evaporator 13. It has become.

  Further, a discharge hole 22c through which the refrigerant compressed in the working chamber 23 is discharged is formed at a substantially central portion of the substrate portion 22a on the fixed scroll 22 side. Further, a discharge chamber 23b communicating with the discharge hole 22c is formed below the discharge hole 22c. Furthermore, a reed valve 23c that functions as a check valve for preventing the refrigerant from flowing back to the working chamber 23 is disposed in the discharge chamber 23b.

  The refrigerant flowing into the discharge chamber 23b is discharged to the outside of the housing 40 through the refrigerant discharge passage 22e formed so as to penetrate the substrate portion 22a on the fixed scroll 22 side and the tubular member 41 of the housing 40. Further, a refrigerant inlet of the oil separator 50 is connected to the refrigerant discharge passage 22e.

  The oil separator 50 separates oil from the refrigerant discharged from the refrigerant discharge passage 22e. In this embodiment, the oil separator 50 employs a centrifugal separation type in which the flow of the refrigerant discharged from the refrigerant discharge passage 22e is swirled to separate the oil by the action of centrifugal force.

  The oil separated by the oil separator 50 is stored in the lower cover member 43 of the housing 40 from the oil outlet 50a provided on the lower side of the oil separator 50 through the oil outlet pipe 51a. It flows out to the chamber 43a side. On the other hand, the refrigerant from which the oil has been separated flows out from the refrigerant outlet 50 b provided on the upper side of the oil separator 50 to the refrigerant inlet side of the water-refrigerant heat exchanger 11.

  The oil stored in the oil storage chamber 43a provided in the lower lid member 43 includes an oil supply pipe 51b, an oil supply passage 22f formed in the substrate portion 22a of the fixed scroll 22, and a throttle passage 22g for reducing the pressure of the oil. In addition, the oil is supplied to the inlet side of the main oil supply passage 25 c positioned on the lower side of the shaft 25 through the oil supply passage 21 d formed in the substrate portion 21 a of the movable scroll 21.

  Next, the detailed configuration of the first and second bearing portions 26 and 27 of the present embodiment will be described. First, the 1st bearing part 26 is demonstrated using FIG. 2 is an enlarged AA sectional view of FIG. 1, and FIG. 3 is an enlarged view of a portion B of FIG.

  The first bearing portion 26 is coaxial with the sliding bearing 261 that rotatably supports the shaft 25, and the outer peripheral side of the annular inner race (inner annular member) 262a and the inner race 262a arranged coaxially with the shaft 25. A rolling bearing 262 for rotating the inner race 262a and the outer race 262b with a plurality of spheres (rolling members) 262c interposed between the annular outer race (outer annular member) 262b disposed above is provided. is doing.

  The sliding bearing 261 is formed of a cylindrical metal, and supports the outer peripheral surface of the shaft 25 by its inner peripheral surface (hereinafter referred to as a bearing surface). On the other hand, the outer peripheral side of the sliding bearing 261 is fixed to the inner peripheral side of the inner race 262a of the rolling bearing 262 by press-fitting. Further, the outer peripheral side of the outer race 262b of the rolling bearing 262 is fixed to the middle housing 44 by press fitting.

  Further, a pin 263a extending in the rotation axis direction is fixed to the upper surface portion of the slide bearing 261 in the rotation axis direction by a fixing means such as press fitting. A plate-like elastic member 263b is fixed to the middle housing 44. The elastic member 263b is formed of a metal plate that spreads perpendicularly to the rotation axis direction and the radial direction of the shaft 25 when it is not elastically deformed.

  More specifically, one end of the elastic member 263b is joined to a cylindrical bush 263c, and this bush 263c is fixed to the middle housing 44 by a rivet 263d. Furthermore, although the other end does not contact the shaft 25, it extends from the middle housing 44 side to a range where it can contact the pin 263a.

  In other words, the pin 263a of this embodiment functions as a contact member that contacts the elastic member 263b. Therefore, when the rotational torque is transmitted from the sliding bearing 261 to the rolling bearing 262 by the frictional force between the outer peripheral surface of the shaft 25 and the bearing surface of the sliding bearing 261 as the shaft 25 rotates, as shown in FIG. Further, the elastic member 263b is elastically deformed by receiving a load from the pin 263a.

  At this time, relative rotation between the inner race 262a and the outer race 262b is restricted while the elastic member 263b and the pin 263a are in contact with each other. Furthermore, when the rotational torque increases and the elastic member 263b is deformed until it cannot contact the pin 263a, relative rotation between the inner race 262a and the outer race 262b is allowed.

  Furthermore, the elastic member 263b of the present embodiment is deformed until the elastic member 263b cannot contact the pin 263a when the rotational torque transmitted from the sliding bearing 261 to the rolling bearing 262 is equal to or higher than a predetermined reference rotational torque. Is set to

  That is, in the present embodiment, the inner race 262a is rotated until the rotational torque transmitted from the sliding bearing 261 to the rolling bearing 262 by the pin 263a, the elastic member 263b, the bush 263c, and the rivet 263d is equal to or higher than a predetermined reference rotational torque. And a rotation restricting means 263 for restricting relative rotation of the outer race 262b.

  As shown in FIG. 1, the second bearing portion 27 is configured as a sliding bearing that rotatably supports the outer peripheral surface of the shaft 25 by its inner peripheral surface (hereinafter referred to as a bearing surface). Furthermore, the 2nd bearing part 27 is being fixed to the cylindrical member 41 of the housing 40 via the interposition member 27a.

  The interposition member 27 a is formed in a shape in which the outer peripheral portion of the annular plate extending in the horizontal direction is bent downward, and the outer peripheral portion is fixed in a state where the outer peripheral portion is in contact with the tubular member 41 of the housing 40. Further, a flange portion 27b that protrudes in the horizontal direction is formed at the upper end portion of the second bearing portion 27, and the flange portion 27b is fastened and fixed onto the interposed member 27a by bolting.

  The refrigeration cycle control device 60 is composed of a well-known microcomputer including a CPU, ROM, RAM and the like and its peripheral circuits, and controls the operation of various devices connected to the output side thereof. Specifically, as shown in FIG. 1, the compressor 10, the electric expansion valve 12, and the like are connected to the output side of the refrigeration cycle control device 60.

  The refrigeration cycle control device 60 is configured such that a control device that controls the compressor 10, the electric expansion valve 12, and the like is integrally configured. The configuration (hardware and software) for controlling the rotational speed (refrigerant discharge capacity) of 10 is the rotational speed control device 60a, and the configuration for controlling the operation (throttle opening) of the electric expansion valve 12 is the variable throttle control device 60b. To do.

  Of course, the rotation speed control device 60a and the variable throttle control device 60b may be configured as separate control devices with respect to the refrigeration cycle control device 60.

  On the other hand, on the input side of the refrigeration cycle control device 60, a discharge temperature sensor as discharge temperature detection means for detecting the temperature of the high-pressure refrigerant discharged from the compressor 10, and evaporation for detecting the low-pressure side refrigerant temperature in the outdoor evaporator 13 are provided. An evaporator temperature sensor as an oven temperature detecting means, an outside air temperature sensor as an outside air temperature detecting means for detecting the outside air temperature for exchanging heat with the low-pressure refrigerant in the outdoor evaporator 13, and the like are connected.

  Further, an operation panel (not shown) is connected to the input side of the refrigeration cycle control device 60, and an operation signal for operating and stopping the heat pump type hot water heater, a hot water supply temperature setting signal for the hot water heater, and the like are input to the refrigeration cycle control device 60. The

  Next, the operation of this embodiment in the above configuration will be described. First, the operation of the heat pump cycle 1 as a whole will be described. When the operation signal of the heat pump type hot water heater is input from the operation panel to the refrigeration cycle control device 60, the refrigeration cycle control device 60 reads the detection signals of the various sensors and the operation signals of the operation panel. And based on the value of a detection signal and an operation signal, the control state output to the various apparatuses connected to the output side is determined.

  And a control signal is output with respect to various apparatuses so that the determined control state may be obtained. After that, until the stop signal of the heat pump type hot water heater is input to the refrigeration cycle control device 60 by the operation panel, the above detection signal and operation signal are read at every predetermined control cycle → control state determination of various devices → various devices A control routine such as outputting a control signal to is repeated.

  Thereby, the compressor 10 operates, the high-temperature high-pressure refrigerant and hot water discharged from the compressor 10 exchange heat in the water-refrigerant heat exchanger 11, and the hot water is heated. At this time, the rotation speed (refrigerant discharge capacity) of the compressor 10 is determined so that the temperature of the high-pressure refrigerant discharged from the compressor 10 becomes the target discharge temperature. This target discharge temperature is determined based on the detection signals of the various sensors described above and the temperature setting signal of the operation panel.

  The refrigerant flowing out of the water-refrigerant heat exchanger 11 is decompressed and expanded by the electric expansion valve 12. At this time, the throttle opening degree of the electric expansion valve 12 is controlled so that the coefficient of performance (COP) of the heat pump cycle 1 approaches the maximum. The refrigerant decompressed and expanded by the electric expansion valve 12 absorbs heat from the outside air in the outdoor evaporator 13 and evaporates. The refrigerant evaporated in the outdoor evaporator 13 is sucked into the compressor 10 and compressed again.

  Next, the operation of the compressor 10 during the operation of the heat pump cycle 1 will be described. During the operation of the heat pump cycle 1, electric power is supplied to the stator coil 31b of the electric motor 30 of the compressor 10, and the rotor 32 and the shaft 25 rotate.

  As a result, the movable scroll 21 undergoes revolving motion (turning motion), and the operation positioned at the outermost periphery in the working chamber 23 formed between the tooth portion 21 b of the movable scroll 21 and the tooth portion 22 b of the fixed scroll 22. Refrigerant and oil are sucked into the chamber 23.

  The refrigerant supplied to the working chamber 23 is compressed as the volume of the working chamber 23 decreases. The sliding parts of the movable scroll 21 and the fixed scroll 22 are lubricated by the oil sucked into the working chamber 23. Further, the refrigerant compressed in the working chamber 23 flows into the oil separator 50 through the discharge chamber 23b and the refrigerant discharge passage 22e together with the oil.

  The refrigerant from which the oil has been separated by the oil separator 50 flows out from the refrigerant outlet 50b to the refrigerant inlet side of the water-refrigerant heat exchanger 11. On the other hand, the oil separated from the refrigerant flows out from the oil outlet 50a and is stored in the oil storage chamber 43a. The oil stored in the oil storage chamber 43a is supplied to the inlet side of the main oil supply passage 25c positioned below the shaft 25 via the oil supply passages 21d and 22f and the throttle passage 22g.

  Further, part of the oil supplied to the inlet side of the main oil supply passage 25c flows into the boss portion 21c and lubricates the sliding portion between the boss portion 21c and the eccentric portion 25b. Further, the remaining oil supplied to the inlet side of the main oil supply passage 25c flows into the main oil supply passage 25c, and from the first and second auxiliary oil supply passages 25d and 25e, respectively, the outer peripheral surface of the shaft 25 and the first and second oil supply passages 25c and 25e. 2 Guided to the sliding portion with the bearing portion 26. Thereby, the sliding part of the 1st, 2nd bearing parts 26 and 27 is lubricated.

  The oil supplied to the sliding portions of the first and second bearing portions 26 and 27 lubricates the sliding portions, and then flows downward in the inner space of the housing 40 by the action of gravity to flow through the refrigerant suction path 100. And flows into the working chamber. And if the stop signal of the heat pump type hot water heater is inputted to the refrigeration cycle control device 60 from the operation panel, the power supply to the stator coil 31b of the electric motor 30 is cut off, and the rotation of the shaft 25 is stopped. That is, the compressor 10 stops.

  As described above, the compressor 10 of the present embodiment operates when heating the hot water supply, and stops operating when the hot water supply is not heated. Therefore, if the compressor 10 is left in a stopped state, the oil film formed between the bearing surfaces of the sliding bearings of the first and second bearing portions 26 and 27 and the outer peripheral surface of the shaft 25 is cut. Therefore, when the compressor 10 is started, there may be a boundary lubrication state where the oil film is cut between the bearing surface and the outer peripheral surface of the shaft 25.

  In such a boundary lubrication state, since the frictional force between the bearing surface of the sliding bearing and the outer peripheral surface of the shaft 25 increases, there is a concern about wear of the bearing surface of the sliding bearing and wear of the outer peripheral surface of the shaft 25.

  On the other hand, in the present embodiment, as the first bearing portion 26, the sliding bearing 261, the rolling bearing 262, and the rotation restricting means 263 configured by the pin 263a, the elastic member 263b, the bush 263c, and the rivet 263d are employed. Therefore, until the rotational torque transmitted from the sliding bearing 261 to the rolling bearing 262 exceeds the reference rotational torque, the outer peripheral surface of the shaft 25 is supported by the sliding bearing 261 having higher reliability than the rolling bearing 262. Can do.

  Further, when the rotational torque transmitted from the slide bearing 261 to the rolling bearing 262 exceeds the reference rotational torque, the inner race 262a and the outer race 262b rotate relative to each other. Can be supported.

  Accordingly, when the rotational torque received by the rolling bearing 262 from the sliding bearing 261 becomes equal to or higher than the reference rotational torque, the slipping force is reduced during an operating condition in which the frictional force between the bearing surface of the sliding bearing 261 and the outer peripheral surface of the shaft 25 increases. The shaft 25 can be supported by the rolling bearing 262 without sliding the bearing surface of the bearing 261 and the outer peripheral surface of the shaft 25.

  Thereby, it is possible to suppress the sliding bearing 261 from being worn and to improve the reliability of the bearing structure of the compression mechanism 20. As a result, the reliability of the compressor 10 as a whole can be improved.

  Furthermore, in this embodiment, since the rotation restricting means 263 is constituted by the pin 263a and the elastic member 263b, the inner race 262a and the outer race 262b rotate relative to each other until the rotational torque becomes equal to or higher than the reference rotational torque. This configuration is very easy, and a configuration that allows the inner race 262a and the outer race 262b to rotate relative to each other when the rotational torque becomes equal to or higher than the reference rotational torque can be realized very easily.

  In addition, after the rotational torque increases until it becomes equal to or higher than the reference rotational torque, when the rotational torque becomes smaller than the reference rotational torque again, the elastic member 263b returns to a shape that abuts against the pin 263a, so the inner race 262a and the outer race 262b are relatively It can regulate that it rotates. In other words, the rotation restricting means 263 can have a restoration function.

  In this embodiment, the pin 263a as the contact member is disposed on the upper surface of the sliding bearing 261 in the rotation axis direction, but the contact member does not change its position relative to the inner race 262a. If it arrange | positions to a member, the effect similar to this embodiment can be acquired. Of course, the contact member may be disposed on the inner race 262a itself.

  In this embodiment, the elastic member 263b is arranged in the middle housing 44. However, if the elastic member 263b is arranged on a member that does not change its position with respect to the outer race 262b, the same effect as in this embodiment is obtained. Obtainable. Of course, the contact member may be disposed on the outer race 262b itself.

(Second Embodiment)
In the present embodiment, as shown in FIG. 4, an example will be described in which rotation amount detection means for detecting the relative rotation amount of the inner race 262a and the outer race 262b is added to the first embodiment. Other configurations are the same as those of the first embodiment. FIG. 4 is an axial sectional view of the compressor 10 corresponding to FIG. 1 of the first embodiment, and the same or equivalent parts as those of the first embodiment are denoted by the same reference numerals. The same applies to the following drawings.

  Specifically, in the present embodiment, a strain gauge 264 that detects the strain amount of the elastic member 263b is employed as the rotation amount detection means. The strain gauge 264 changes the resistance value according to the deformation amount (strain amount) of the elastic member 263b, and forms a bridge circuit (not shown) to convert the deformation amount of the elastic member 263b into an electric signal. Furthermore, the strain gauge 264 is connected to the input side of the refrigeration cycle control device 60.

  Next, the operation of this embodiment in the above configuration will be described. The basic operation of the heat pump cycle 1 in the present embodiment is the same as in the first embodiment. Further, in the present embodiment, when the refrigeration cycle control device 60 reads the detection signals of various sensors and the operation signals of the operation panel, the output signal of the strain gauge 264, that is, the relative rotation amount between the inner race 262a and the outer race 262b. Read the detected value.

  And the control state output to the various apparatuses connected to the output side is determined based on the value of a detection signal and an operation signal similarly to 1st Embodiment. Further, in the present embodiment, when the rotational speed control device 60a constituting the refrigeration cycle control device 60 has a relative rotational amount detected by the strain gauge 264 equal to or greater than a predetermined reference relative rotational amount, The control state of the compressor 10 is corrected so as to reduce the rotational speed.

  More specifically, when the relative rotation amount detected by the strain gauge 264 becomes equal to or greater than a predetermined reference relative rotation amount, the rotation speed of the shaft 25 decreases with an increase in the detected relative rotation amount. The control state of the compressor 10 is corrected so as to increase the amount. The reference relative rotation amount is set in a range in which the elastic member 263b can contact the pin 263a even if the elastic member 263b is elastically deformed.

  And a control signal is output with respect to various apparatuses so that the determined control state may be obtained. After that, until the stop signal of the heat pump type hot water heater is input to the refrigeration cycle control device 60 by the operation panel, the above detection signal and operation signal are read at every predetermined control cycle → control state determination of various devices → various devices A control routine such as outputting a control signal to is repeated. Other operations are the same as those in the first embodiment.

  As described above, in the heat pump cycle 1 of the present embodiment, when the relative rotation amount detected by the strain gauge 26 becomes equal to or greater than a predetermined reference relative rotation amount, the rotation number of the shaft 25 is decreased to reduce the first rotation amount. The rotational torque that the rolling bearing 262 of the bearing portion 26 receives from the sliding bearing 261 can be reduced.

  Therefore, in the first bearing portion 26, the frequency with which the relative rotation between the inner race 262a and the outer race 262b of the rolling bearing 262 is allowed to be reduced is reduced, and the shaft 25 is moved by the sliding bearing 261 having higher reliability than the rolling bearing 262. It is easy to maintain the supporting state.

  Further, even when the rotational speed control device 60a reduces the rotational speed of the shaft 25 and the rotational torque does not decrease, the first bearing portion 26 has the inner race 262a and the outer side as in the first embodiment. The race 262 b rotates relatively, and the shaft 25 can be supported by the rolling bearing 262. Therefore, the sliding bearing 261 can be prevented from being worn.

  As described above, according to the rotation speed control device 60a of the present embodiment, the reliability of the bearing structure of the compression mechanism 20 can be improved. As a result, the reliability of the compressor 10 as a whole can be improved.

(Third embodiment)
This embodiment demonstrates the example which changed the control aspect of the refrigerating-cycle control apparatus 60 in 2nd Embodiment. The configurations of the heat pump cycle 1 and the compressor 10 of the present embodiment are the same as those of the second embodiment.

  Specifically, in this embodiment, when the heat pump cycle 1 is operated, the refrigeration cycle control device 60 reads the values of the detection signal and the operation signal as in the second embodiment, and the detected signal and the operation signal are read. Based on the value, the control state to be output to various devices connected to the output side is determined.

  Furthermore, in this embodiment, when the refrigeration cycle control device 60 (specifically, the variable throttle control device 60b) has a relative rotation amount detected by the strain gauge 264 equal to or greater than a predetermined reference relative rotation amount. The control state of the electric expansion valve 12 is corrected so that the throttle opening of the electric expansion valve 12 is increased.

  More specifically, when the relative rotation amount detected by the strain gauge 264 is equal to or greater than a predetermined reference relative rotation amount, the throttle of the electric expansion valve 12 increases as the detected relative rotation amount increases. The control state of the electric expansion valve 12 is corrected so as to increase the opening amount. And a control signal is output with respect to various apparatuses so that the determined control state may be obtained.

  After that, until the stop signal of the heat pump type hot water heater is input to the refrigeration cycle control device 60 by the operation panel, the above detection signal and operation signal are read at every predetermined control cycle → control state determination of various devices → various devices A control routine such as outputting a control signal to is repeated. Other operations are the same as those in the first embodiment.

  Since the heat pump cycle 1 of the present embodiment operates as described above, when the relative rotation amount detected by the strain gauge 26 becomes equal to or larger than a predetermined reference relative rotation amount, the throttle opening degree of the electric expansion valve 12 is increased. And the pressure difference between the suction side refrigerant pressure and the discharge side refrigerant pressure of the compression mechanism 20 can be reduced. Thereby, the rotational torque which the rolling bearing 262 of the 1st bearing part 26 receives from the sliding bearing 261 can be reduced.

  Therefore, as in the second embodiment, in the first bearing portion 26, it is easy to maintain a state in which the shaft 25 is supported by the sliding bearing 261 having higher reliability than the rolling bearing 262. Further, even when the refrigeration cycle control device 60 increases the throttle opening of the electric expansion valve 12 and the rotational torque does not decrease, the shaft 25 is supported by the rolling bearing 262 as in the first embodiment. Thus, it is possible to suppress the sliding bearing 261 from being worn.

  As described above, according to the refrigeration cycle control device 60 of the present embodiment, the reliability of the bearing structure of the compression mechanism 20 can be improved. As a result, the reliability of the compressor 10 as a whole can be improved. In addition, the throttle opening degree of the electric expansion valve 12 is increased when the rotational speed control device 60a of the second embodiment is combined with the present embodiment and the relative rotational speed is equal to or greater than a predetermined reference relative rotational speed. In addition, the rotational speed of the shaft 25 may be reduced.

(Fourth embodiment)
In 1st Embodiment, although the example which employ | adopted the rotation control means 263 comprised by the pin 263a, the elastic member 263b, the bush 263c, and the rivet 263d was demonstrated, in this embodiment, as shown to FIGS. An example in which the member 263b is abolished and a connecting member 263e that connects the inner race 262a and the outer race 262b is employed will be described. 5 to 7 are drawings corresponding to FIGS. 1 to 3 of the first embodiment, FIG. 6 is an enlarged CC cross-sectional view of FIG. 5, and FIG. FIG.

  Specifically, the connecting member 263e of the present embodiment is configured by a rod-shaped member extending from the outer race 262b to the pin 263a of the inner race 262a, and the rotational torque received by the rolling bearing 262 from the sliding bearing 261 is the reference rotation. The strength is set so that it breaks when the torque is exceeded.

  The end of the connecting member 263e on the outer race 262b side is joined to a bush 263c, as in the first embodiment, and this bush 263c is fixed to the middle housing 44 by a rivet 263d. Further, two arms are provided at the end on the inner race 262a side, and a pin 263a is fitted between the two arms.

  In the present embodiment, in the first bearing portion 26, the relative rotation of the inner race 262a and the outer race 262b can be restricted by the connecting member 263e until the rotational torque becomes equal to or higher than the reference rotational torque. Therefore, the shaft 25 can be supported by the sliding bearing 261 having higher reliability than the rolling bearing 262.

  Further, when the rotational torque becomes equal to or higher than the reference rotational torque, the connecting member 263e is broken, so that relative rotation between the inner race 262a and the outer race 262b is allowed. Accordingly, the shaft 25 can be supported by the rolling bearing 262.

  According to this embodiment, not only can the rotation restricting means be realized with a very simple configuration, but the shaft 25 is supported by the rolling bearing even when the sliding bearing 261 and the shaft 25 are locked by seizure. Therefore, the reliability of the compressor 10 as a whole can be effectively improved.

(Fifth embodiment)
This embodiment demonstrates the example which changed the control aspect of the refrigerating-cycle control apparatus 60 in 2nd Embodiment. The configurations of the heat pump cycle 1 and the compressor 10 of the present embodiment are the same as those of the second embodiment. Specifically, in this embodiment, the control mode at the time of starting and stopping of the heat pump cycle 1 is changed with respect to the second embodiment.

  As described above, when the hot water is not heated and the compressor 10 is left in a stopped state, the bearing surfaces of the sliding bearings of the first and second bearing portions 26 and 27 and the outer peripheral surface of the shaft 25 are not affected. The oil film formed between them tends to break. Further, immediately after the compressor 10 is started, the rotational speed of the shaft 25 is low, and the sliding speed between the bearing surface of the sliding bearing of the first and second bearing portions 26 and 27 and the outer peripheral surface of the shaft 25 is low. It is difficult to form an oil film between the surface and the outer peripheral surface.

  Therefore, when the compressor 10 is started, for example, if the rotational speed of the shaft 25 is increased at a predetermined reference increase degree, the bearing surfaces of the slide bearings of the first and second bearing portions 26 and 27 and the shaft 25 There is a concern that an oil film cannot be formed between the outer peripheral surface and the rotational torque received by the rolling bearing 262 of the first bearing portion 26 from the sliding bearing 261 increases. The degree of increase in the number of rotations means the amount of increase in the number of rotations per unit time.

  Therefore, in the present embodiment, as shown in the time chart of FIG. 8A, the relative rotation amount θ detected by the strain gauge 264 when the compressor 10 is started is equal to or greater than the reference relative rotation amount Kθ. At this time, the refrigeration cycle control device 60 (specifically, the rotational speed control device 60a) decreases the increasing rate of increasing the rotational speed of the shaft 25 at the time of activation.

  Thereby, in this embodiment, the rotational torque which the rolling bearing 262 of the 1st bearing part 26 receives from the sliding bearing 261 at the time of starting of the compressor 10 can be reduced. As a result, the same effect as that of the second embodiment can be obtained even when the compressor 10 is started.

  Further, as shown in the time chart of FIG. 8B, when the compressor 10 is started and the relative rotation amount is equal to or larger than a predetermined reference relative rotation amount Kθ, the electric expansion valve is used. The same effect can be obtained by increasing the aperture opening E of 12.

  On the other hand, when the compressor 10 is stopped, as shown in the time chart of FIG. 9A, if the rotation of the shaft 25 is stopped, the relative rotation amount θ may become equal to or greater than the reference relative rotation amount Kθ. is there. Therefore, in the present embodiment, as shown in the time chart of FIG. 9B, when the compressor 10 is stopped, the relative rotation amount θ detected by the strain gauge 264 is gradually increased so as not to exceed the reference relative rotation amount. After reducing the rotation speed of the compressor 10, it is stopped.

  Thereby, in this embodiment, even when the compressor 10 stops, the rotational torque which the rolling bearing 262 of the 1st bearing part 26 receives from the sliding bearing 261 can be reduced. As a result, the same effect as in the second embodiment can be obtained. Further, as shown in the time chart of FIG. 9B, the throttle opening degree of the electric expansion valve 12 may be increased as the rotational speed of the compressor 10 decreases.

(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.

  (1) In the above-described embodiment, the bearing structure of the rotary machine of the present invention configured by the sliding bearing 261, the rolling bearing 262, and the rotation restricting means 263 is applied to the bearing structure of the compression mechanism 20. The application of is not limited to this. For example, a blower mechanism, an electric motor, a generator, an engine, or the like may be adopted as the rotating machine and applied to these bearing structures.

  Further, the compression mechanism 20 of the compressor 10 is not limited to the scroll type, and is a rolling piston type compression mechanism, a plurality of cylinders and pistons arranged in the circumferential direction, and a fluid is sequentially compressed and discharged by each cylinder and piston. Any compression mechanism having a shaft 25 that is rotatably supported may be used, such as a reciprocating compression mechanism. Further, the compressor 10 is not limited to an electric compressor, and for example, the bearing structure for a rotary machine of the present invention may be applied to an engine-driven compressor using an engine or the like as a drive source.

  (2) In the above-described embodiment, the bearing structure of the rotary machine of the present invention is applied to the first bearing portion 26, but of course the second bearing portion 27 may be applied. Further, in a rotary machine having a plurality of bearing portions, it may be applied to at least one of the plurality of bearing portions, or may be applied to all.

  (3) In the above-described embodiment, the example in which the refrigeration cycle control device of the present invention is applied to the heat pump cycle 1 for heating hot water supply has been described. Of course, the rotation speed control device and the refrigeration cycle control device of the present invention are used. The present invention may be applied to a refrigeration cycle for an air conditioner, a refrigeration cycle for a refrigerator or a freezer.

  Furthermore, although the above-mentioned embodiment demonstrated the example which employ | adopted the carbon dioxide as a refrigerant | coolant of the heat pump cycle (refrigeration cycle) 1, the kind of refrigerant | coolant is not limited to this. Ordinary fluorocarbon refrigerants, hydrocarbon refrigerants, and the like may be employed. Furthermore, the heat pump cycle 1 may constitute a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant.

  Furthermore, the rotation speed control device of the present invention is not limited to the refrigeration cycle, and can be widely applied to devices including a rotating machine.

  (4) In the above-described embodiment, the example in which the strain gauge 264 is used as the rotation amount detection unit that detects the relative rotation amount between the inner race 262a and the outer race 262b has been described. However, the rotation amount detection unit is not limited thereto. . For example, detection means for directly detecting the relative rotation between the inner race 262a and the outer race 262b may be employed.

  As such a detecting means, specifically, a laser that forms a plurality of axially extending grooves on the outer peripheral surface of the inner race 262a and detects the movement of the grooves on the outer race 262b side by the amount of reflected laser light. It is possible to adopt a configuration in which a type detection device or a magnetic detection device (magnet pickup, MRE element, etc.) that detects magnetic fluctuations due to the movement of the groove is arranged.

20 Compression mechanism (rotary machine)
25 Shaft (Rotating shaft)
261 Slide bearing 262 Rolling bearing 262a Inner race 262b Outer race 262c Rolling body 263 Rotation restricting means 263a Pin 263b Elastic member 263e Connecting member 264 Strain gauge (Rotation amount detecting means)
60 refrigeration cycle control device 60a rotation speed control device

Claims (7)

A sliding bearing (261) that rotatably supports a rotating shaft (25) of the rotating machine (20);
A rolling bearing (262) for rotating the inner annular member (262a) and the outer annular member (262b) relative to each other with a rolling element (262c) interposed between the inner annular member (262a) and the outer annular member (262b). And
The sliding bearing (261) is fixed to the inner annular member (262a),
Further, the inner annular member (262a) and the outer annular member (262b) are moved until the rotational torque transmitted from the sliding bearing (261) to the rolling bearing (262) becomes equal to or higher than a predetermined reference rotational torque. A bearing structure for a rotary machine, comprising: a rotation restricting means (263) for restricting relative rotation.   The bearing structure for a rotary machine according to claim 1, further comprising a rotation amount detecting means (264) for detecting a relative rotation amount between the inner annular member (262a) and the outer annular member (262b). . The rotation restricting means (263) includes a plate-like elastic member (263b) fixed to the outer annular member (262b) side and elastically deforming as the rotational torque increases, and the inner annular member (262a). It has a contact member (263a) fixed to the side and abutted against the elastic member (263b),
The rotary machine according to claim 2, wherein the elastic member (263b) is configured to contact the contact member (263a) until the rotational torque becomes equal to or greater than the reference rotational torque. Bearing structure.   The bearing structure for a rotary machine according to claim 3, wherein the rotation amount detecting means is constituted by a strain gauge (264) for detecting a strain amount of the elastic member (263b). The rotation restricting means (263) includes a connecting member (263e) that connects the outer annular member (262b) side and the inner annular member (262a) side,
The bearing structure for a rotary machine according to claim 1, wherein the connecting member (263e) is formed so as to be broken when the rotational torque becomes equal to or greater than the reference rotational torque. A rotational speed control device for controlling the rotational speed of the rotary shaft (25) of the rotary machine (20) to which the bearing structure of the rotary machine according to claim 2 is applied,
Rotational speed control characterized in that the rotational speed of the rotary shaft (25) is reduced when the relative rotational quantity detected by the rotational quantity detection means (264) is equal to or greater than a predetermined reference relative rotational quantity. apparatus. The refrigerating cycle control which controls the action | operation of the refrigerating cycle (1) provided with the compression mechanism (20) to which the bearing structure of the rotary machine of Claim 2 was applied, and the variable throttle mechanism (12) which decompresses and expands a high-pressure refrigerant | coolant. A device,
Refrigeration characterized in that the throttle opening of the variable throttle mechanism (12) is increased when the relative rotational amount detected by the rotational amount detecting means (264) is equal to or greater than a predetermined reference relative rotational amount. Cycle control device.

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