Reciprocating compressor

Abstract

To provide a reciprocating compressor capable of finely adjusting a suction amount of gas in a cylinder.SOLUTION: A reciprocating compressor 10 comprises: a cylinder 40 forming a cylinder chamber Sc; and a movable part 60 that includes a suction valve 63 provided around the cylinder chamber Sc, and at least one of a suction valve seat 61 configured to seat the suction valve 63 and a back member 65 located on the side opposite to the suction valve seat 61 with the suction valve 63 interposed therebetween, and that is configured to move in an axial direction of the cylinder 40; and an actuator 100 that moves the movable part 60 in the axial direction to change a movable range of the suction valve 63 between the suction valve seat 61 and the back member 65.SELECTED DRAWING: Figure 2

Description

Technical Field

[0001] The present disclosure relates to a reciprocating compressor.

Background Art

[0002] Conventionally, a reciprocating compressor capable of changing its operating state is known. For example, in Patent Document 1, it is possible to keep the suction valve of the reciprocating compressor open, and the operating state of the reciprocating compressor switches from a loaded operating state to an unloaded operating state.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] However, in the above patent document, it is difficult to finely adjust the gas intake amount in at least one of the plurality of cylinders provided in the reciprocating compressor. Therefore, there is a possibility that the reciprocating compressor cannot perform a suitable operation according to the usage conditions.

[0005] An object of the present disclosure is to provide a reciprocating compressor capable of finely adjusting the gas intake amount in a cylinder.

Means for Solving the Problems

[0006] The reciprocating compressor according to at least one embodiment of the present disclosure includes a cylinder forming a cylinder chamber, a suction valve provided around the cylinder chamber, A movable part, which includes either an intake valve seat on which the intake valve is seated, or a rear member located on the opposite side of the intake valve seat with the intake valve in between, and which is configured to move in the axial direction of the cylinder, An actuator moves the movable part in the axial direction and changes the range of motion of the intake valve between the intake valve seat and the back member. It is equipped with. [Effects of the Invention]

[0007] According to this disclosure, a reciprocating compressor can be provided that can finely adjust the amount of gas intake in a cylinder. [Brief explanation of the drawing]

[0008] [Figure 1] This is a conceptual cross-sectional view of a reciprocating compressor according to one embodiment. [Figure 2] This is a conceptual cross-sectional view showing a reciprocating compressor according to the first embodiment. [Figure 3] This is a cross-sectional view conceptually showing the adjustment range of the movable range of an intake valve according to one embodiment. [Figure 4A] This is an explanatory diagram conceptually showing the gas intake stroke of a reciprocating compressor in a second state according to one embodiment. [Figure 4B] This is an explanatory diagram conceptually illustrating the gas intake stroke of a reciprocating compressor, following Figure 4A. [Figure 5] This is a conceptual perspective view showing a cylinder according to one embodiment. [Figure 6] This is an explanatory diagram conceptually showing multiple cylinders according to one embodiment. [Figure 7] This is a conceptual cross-sectional view showing a reciprocating compressor according to the second embodiment. [Figure 8] This is a conceptual cross-sectional view showing another reciprocating compressor according to the second embodiment. [Modes for carrying out the invention]

[0009] Hereinafter, several embodiments of this disclosure will be described with reference to the attached drawings. However, the dimensions, materials, shapes, relative arrangements, etc., of the components described or shown in the drawings as embodiments are not intended to limit the scope of this disclosure, but are merely illustrative examples. For example, expressions describing relative or absolute arrangements such as "in a certain direction," "along a certain direction," "parallel," "orthogonal," "center," "concentric," or "coaxial" should not only strictly describe such arrangements, but also describe states of relative displacement with tolerances or angles or distances that allow for the same function to be achieved. For example, expressions such as "identical," "equal," and "homogeneous" that describe things being in an equal state not only describe a state of being strictly equal, but also describe a state in which there is a tolerance or a difference that is sufficient to achieve the same function. For example, expressions describing shapes such as squares or cylinders shall not only represent geometrically precise shapes such as squares or cylinders, but also shapes that include protrusions, chamfers, etc., to the extent that the same effect can be achieved. On the other hand, expressions such as "possessing," "including," or "having" one component are not exclusive expressions that exclude the existence of other components. Note that similar configurations may be denoted by the same reference numerals and their explanations may be omitted.

[0010] <1. Overview of the reciprocating compressor 10> Figure 1 is a conceptual cross-sectional view of a reciprocating compressor 10 (hereinafter sometimes referred to as "compressor 10") according to one embodiment of the present disclosure. The compressor 10 is incorporated into a refrigeration cycle that includes, for example, a plurality of heat exchangers such as a condenser and an evaporator. Examples of refrigeration cycles include a binary refrigeration cycle, a two-stage compression refrigeration cycle, or a reverse Brayton refrigeration cycle. In this case, the gas compressed by the compressor 10 is a refrigerant gas. In other embodiments, the compressor 10 may be incorporated into an internal combustion engine or the like, and the gas compressed by the compressor 10 may be combustion gas or the like.

[0011] The compressor 10 according to an embodiment of the present disclosure includes a crankcase 16 and a plurality of cylinders 40 housed in the crankcase 16. Each cylinder 40 forms an inner cylinder chamber Sc in which a piston 42 is housed. Each piston 42 is connected to a crankshaft 48 supported by a bearing 50 provided in the crankcase 16 via a connecting rod 52 or the like. One end of the crankshaft 48 is connected to a motor 54, and each piston 42 can reciprocate inside each cylinder 40 by driving the motor 54. In the exemplary embodiment shown in FIG. 1, two cylinders 40 are provided in parallel, and the pistons 42 in the two cylinders 40 are connected to the crankshaft 48 so as to reciprocate with a phase difference of 180° at the rotation angle of the crankshaft 48. In the following description, the axial direction of the cylinder 40 may be simply referred to as the "axial direction". In the present embodiment, the axial direction coincides with the vertical direction, and the crankshaft 48 extends in the horizontal direction.

[0012] A valve plate 44 for supporting the discharge valve 12 is provided on one end side of the cylinder 40 (the upper end side of the cylinder 40 in FIG. 1). A frustum-shaped discharge valve sheet 70 is disposed inside the opening formed in the valve plate 44. The discharge valve sheet 70 is coupled to the valve cage 66 by bolts 68, and the discharge valve 12 is held between the discharge valve sheet 70 and the valve cage 66. The valve cage 66 is urged toward the cylinder 40 by a head spring 64. Further, the discharge valve 12 is urged toward the discharge valve sheet 70 by a valve spring (not shown) housed in a spring hole 69 provided in the valve cage 66.

[0013] The compressor 10 according to an embodiment of the present disclosure further includes an intake valve 63 provided around the cylinder chamber Sc of the cylinder 40 and an intake valve seat 61 (see FIG. 2) configured such that the intake valve 63 seats thereon. The intake valve 63 is in the shape of an O-ring that continuously extends across the circumferential direction with respect to the axis of the cylinder 40. In other embodiments, the intake valve 63 may be a plurality of plate valves arranged along the circumferential direction.

[0014] The general operation of the compressor 10 shown in FIG. 1 is as follows. As the piston 42 descends with the driving of the motor 54 and the sealed space in the cylinder chamber Sc is decompressed, the pressure in the intake space Si formed outside the cylinder 40 is slightly higher than the pressure in the sealed space. The intake valve 63 seated on the intake valve seat 61 is pushed up, and the gas in the intake space Si is inhaled into the cylinder chamber Sc through the intake valve seat 61. Then, the piston 42 finishes descending and starts ascending. As a result of the gas being compressed by the piston 42 and the sealed space being pressurized, the intake valve 63 is pushed down and seats on the intake valve seat 61. When the piston 42 further ascends and the pressure in the sealed space is slightly higher than the pressure in the discharge space Sd, the discharge valve 12 is pushed up, and the compressed gas in the cylinder chamber Sc is discharged into the discharge space Sd.

[0015] In the present embodiment, the movable range of the intake valve 63 during the operation of the compressor 10 is configured to be changed. The change in the movable range can be achieved by moving either one of the intake valve seat 61 or the back member 65 (described later) in the axial direction. Hereinafter, the compressor 10A(10) according to the first embodiment configured to move the intake valve seat 61 and the compressors 10B, 10C(10) according to the second embodiment configured to move the back member 65 will be exemplified in order.

[0016] <2. Compressor 1*0A(10) According to the First Embodiment> Referring to Figures 2 to 6, an example of a compressor 10A(10) according to the first embodiment is shown. Figure 2 is a conceptual cross-sectional view showing a cylinder 40 of a compressor 10A according to one embodiment of the present disclosure. Figure 3 is a conceptual cross-sectional view showing the adjustment range of the movable range of an intake valve 63 according to one embodiment of the present disclosure. Figures 4A and 4B are conceptual explanatory diagrams showing the stroke when a compressor 10A in a second state according to one embodiment of the present disclosure is drawing in gas. Figure 5 is a conceptual perspective view showing a cylinder 40 according to one embodiment of the present disclosure. Figure 6 is a conceptual explanatory diagram showing a plurality of cylinders 40 according to one embodiment of the present disclosure.

[0017] <2-1. Overview of the 10A Compressor Configuration> As shown in Figure 2, in the first embodiment, the intake valve seat 61A (61) described above is a separate component from the outer circumference of the cylinder 40 and is configured to move in the axial direction. The intake valve seat 61A can be mounted on a flange 47 provided on the opposite side from the intake valve 63. The flange 47 is formed integrally with the outer circumference of the cylinder 40, for example, and is an O-ring shape that extends continuously in the circumferential direction around the entire circumference of the cylinder 40. Multiple passages 47A (see Figure 5) for the gas drawn into the cylinder chamber Sc are arranged along the circumferential direction of the cylinder 40 on this flange 47.

[0018] In this embodiment, the intake valve seat 61A is provided between the outer circumference of the cylinder 40 and an opening provided in the crankcase 16. An inner sealing member 19 is fitted into a groove formed around the entire circumference of the outer circumference of the cylinder 40. The inner sealing member 19 is configured to restrict the passage of gas between the cylinder 40 and the intake valve seat 61A. The inner sealing member 19 is, for example, an elastically deformable O-ring and is pressed against the intake valve seat 61A. Furthermore, an outer sealing member 17 is fitted into a groove formed around the entire circumference of the outer periphery of the intake valve seat 61A. The outer sealing member 17 is configured to restrict the passage of gas between the intake valve seat 61A and the crankcase 16. The outer sealing member 17 is, for example, an elastically deformable O-ring that presses against the crankcase 16.

[0019] The compressor 10A shown in Figure 2 includes a back member 65A (65) located on the opposite side of the intake valve seat 61A from the intake valve 63. The back member 65A in the first embodiment is the same member as the valve plate 44 described above and is fixed in a predetermined position. For example, the intake valve 63, which is pushed up from the intake valve seat 61, comes into contact with the back member 65A. The range of motion of the intake valve 63 corresponds to dimension Rm. The back member 65A also faces radially inward of the cylinder 40 and includes an intake valve guide surface 67 configured to guide the intake valve 63 in the axial direction. This allows the intake valve seat 61 to move stably in the axial direction. In other embodiments, for example, a spring may be interposed between the rear member 65A and the intake valve 63, in which case the intake valve 63 does not need to be in contact with the rear member 65A.

[0020] As described above, in the first embodiment, the intake valve seat 61A is configured to move axially, while the intake valve seat 61A is configured to move axially than the rear member 65A. As a result, the seating position of the intake valve seat 61 is adjusted axially, and the range of motion of the intake valve 63 located between the intake valve seat 61A and the rear member 65A is changed. In the following description of the first embodiment, the intake valve seat 61A may be referred to as the "movable part 60A". The movable part 60A (60) is moved by an actuator 100A, which is a component of the compressor 10A. Details of the actuator 100A will be described later.

[0021] Referring to Figure 3, the switching of the range of motion of the intake valve 63 due to the movement of the movable part 60A will be explained. The compressor 10A changes between a first state in which the intake valve seat 61A, which is the movable part 60A, is placed on the flange 47, and a second state in which the intake valve seat 61A is separated from the flange 47. The amount of adjustment of the range of motion of the intake valve 63 at this time corresponds to dimension Rd. Dimension Rd is equal to the separation distance between the intake valve seat 61A and the flange 47 in the second state. When the compressor 10A is in the second state, the range of motion of the intake valve 63 is narrower than in the first state. As will be described in detail later, in this case the amount of gas intake of cylinder 40 is reduced.

[0022] <2-2. Suction operation of compressor 10A when gas intake volume is reduced> Referring to Figures 4A and 4B, the strokes per cycle in which cylinder 40 of compressor 10A in the second state draws in gas will be explained. Figures 4A and 4B conceptually illustrate the mechanism including cylinder 40 in an axial view of the crankshaft 48. In the following explanation of the gas intake stroke, the influence of the biasing forces of the head spring 64 and valve springs, as explained with reference to Figure 1, will not be considered. In addition, the influence of the self-weight of various components such as the piston 42, intake valve 63, discharge valve 12, and valve cage 66 will not be considered.

[0023] As shown in Figure 4A, when the piston 42 descends, the pressure (Pc) in the sealed space within the cylinder chamber Sc decreases to below the pressure (Pi) in the intake space Si. At this time, the intake valve 63 is pushed up from the intake valve seat 61A, and the intake gas passage Ci is opened (stroke 1). The gas in the intake space Si flows into the cylinder chamber Sc by passing through the intake valve seat 61 and the intake gas passage Ci in sequence. As the piston 42 descends further towards the lower end of its range of motion, the gas is further drawn into the cylinder chamber Sc (stroke 2). Here, when the compressor 10A is in the second state, the flow rate of gas drawn into the cylinder chamber Sc is limited compared to the first state because the cross-sectional area of ​​the intake gas passage Ci is small.

[0024] As shown in Figure 4B, when the crankpin 53 passes bottom dead center and the piston 42 begins to rise, the sealed space within the cylinder chamber Sc is pressurized (stroke 3). If the compressor 10A is in the first state, for example, and sufficient gas has been drawn into the cylinder chamber Sc at stroke 2, then immediately after the piston 42 begins to rise, the pressure in the sealed space within the cylinder chamber Sc (Pc) will be equal to or greater than the pressure in the intake space Si (Pi). However, if the compressor 10A is in the second state, sufficient gas has not been drawn into the cylinder chamber Sc, so the timing at which the pressure in the sealed space (Pc) becomes equal to or greater than the pressure in the intake space Si (Pi) is delayed. As a result, the timing at which the intake valve 63 seats on the intake valve seat 61A is delayed, resulting in a so-called delayed closing of the intake valve 63 (stroke 4). As previously described, the discharge stroke of cylinder 40, which occurs after the intake stroke, is low because the amount of gas intake in cylinder 40 is small. Therefore, the volumetric efficiency of compressor 10A is lower than in the first state. In other words, the output of compressor 10A is low.

[0025] However, when the piston 42 is moving upward (strokes 3 and 4), the pressure in the cylinder chamber Sc is not sufficiently high, so the load on the piston 42 is lower than in the first state. Consequently, the output torque required by the motor 54 driving the piston 42 is reduced, and the power consumption of the motor 54 is reduced. Also, because the output torque required by the motor 54 is reduced, the mechanical losses when the piston 42 reciprocates using the power of the motor 54 are reduced. Therefore, under conditions where the degree of power reduction of the motor 54 is greater than the degree of power reduction of the compressor 10A, the adiabatic efficiency of the compressor 10A is improved. Therefore, in the second state, compressor 10A has a lower output compared to the first state, but it is possible to operate it with high efficiency while reducing power consumption.

[0026] Although detailed illustrations are omitted, in an embodiment in which the compressor 10A is incorporated into a refrigeration cycle, the compressor 10A operates in a first state when the refrigeration system, which utilizes the cold energy obtained by the refrigeration cycle, is started up. At this time, advantages such as a reduction in the time required for the circulating refrigerant to cool to a specified temperature are obtained because the output of the compressor 10A is high. Furthermore, when the refrigeration system is operating at its rated capacity, the output required of the compressor 10A is relatively low, so the compressor 10A operates in a second state. This provides advantages such as reducing the power consumption of the refrigeration system during rated operation. The specific examples of when the compressor 10A switches to the first or second state are not limited to those described above. For example, if the heat load applied to the refrigeration system during rated operation changes, the compressor 10A may temporarily switch from the second state to the first state. This allows the refrigeration system to respond quickly to changes in the heat load. To give yet another example, depending on the specifications of the refrigeration system, such as the type of circulating refrigerant and the operating conditions of the heat exchangers that make up the refrigeration cycle, the compressor 10A may be operated steadily in either the first or second state. In this way, the compressor 10A can appropriately perform according to the type of refrigeration system into which it is incorporated, achieving high versatility for the compressor 10A.

[0027] As described above, the compressor 10A is equipped with an actuator 100A that moves the movable part 60A, which is the intake valve seat 61A, in the axial direction. The actuator 100A changes the range of motion of the intake valve 63 between the intake valve seat 61A and the back member 65A, and changes the cross-sectional area of ​​the intake gas flow path Ci formed between the intake valve 63 and the intake valve seat 61A when the actuator is activated. Thus, a compressor 10A is realized that can adjust the amount of gas intake in cylinder 40 in stages. Therefore, the compressor 10A can be adapted to various operating conditions, such as operating conditions where high output is required or operating conditions where power consumption must be reduced.

[0028] Furthermore, the output control of the compressor 10A can also be performed by so-called unloader control, which involves running one of the cylinders 40 dry (no-load operation). This can be achieved by providing an unloader mechanism configured to keep the intake valve 63 constantly separated from the intake valve seat 61A (61) while the piston 42 is moving up and down. However, when the operating state of the cylinders 40 switches between loaded operation and no-load operation, the difference in the gas discharge amount of the compressor 10A is large, making fine output control of the compressor 10A difficult (for example, if the number of cylinders 40 mounted on the compressor 10A is eight, the output of the compressor 10A will have to be controlled in 12.5% ​​increments, making fine output control difficult). Therefore, if unloader control is performed to reduce the output of the compressor 10A, for example, there is a risk that the output will drop excessively below the appropriate value. In this regard, the present disclosure makes it possible to adjust the load operating state in one cylinder 40 by adjusting the range of motion of the intake valve 63, thereby enabling fine adjustment of the output of the compressor 10A. In addition to the mechanism for adjusting the range of motion of the intake valve 63, the compressor 10A of the present disclosure may also be equipped with an unloader mechanism.

[0029] Furthermore, while the output of the compressor 10A can also be controlled by controlling the rotational speed of the motor 54, this requires the installation of an inverter to control the frequency of the power supplied to the motor 54, which may lead to increased costs for the compressor 10A. In this disclosure, however, the installation of an inverter is not essential, making it possible to achieve fine output control while suppressing the increase in the cost of the compressor 10A.

[0030] In this embodiment, the movable part 60A, which is the intake valve seat 61A, is ring-shaped and extends continuously along the circumferential direction of the cylinder 40. As a more specific example, the movable part 60A is O-ring shaped and extends continuously around the entire circumference of the cylinder 40. This reduces the number of parts constituting the compressor 10A compared to the case where multiple movable parts 60A are arranged along the circumferential direction (more specifically, when the intake valve 63 is a reed valve), thus simplifying the configuration of the actuator 100A.

[0031] Furthermore, in this embodiment, the movable part 60A, which is configured to move in the axial direction, corresponds to the intake valve seat 61, rather than the rear member 65A, and there is no need to move the rear member 65A in the axial direction. As a result, the actuator 100A can be simplified in its configuration.

[0032] Furthermore, the rear member 65A includes an intake valve guide surface 67 configured to guide the intake valve 63 in the axial direction. This ensures that the intake valve 63 can operate stably even when the axial distance between the intake valve seat 61 and the rear member 65A is changed by the actuator 100.

[0033] <2-3. Details of the Actuator 100A Configuration> Refer to Figures 2, 3, 5, and 6 to illustrate the details of the configuration of actuator 100A(100).

[0034] As shown in Figures 2 and 3, in this embodiment, the actuator 100A includes a drive source 150A (150) and a moving member 20A (20) that moves the movable part 60A by the driving force transmitted from the drive source 150A. The moving member 20A can narrow and widen the range of motion of the intake valve 63 by moving the movable part 60A, and is located on the side of the movable part 60A relative to the intake valve 63 (in the example of Figure 3, on the lower side relative to the intake valve 63). As a more specific example, the moving member 20A is provided on the outer circumference of the cylinder 40 on the opposite side from the rear member 65A, with the intake valve seat 61A in between. In this embodiment, the movable member 20A is a pin that extends in the axial direction, as will be described later. In other embodiments, the movable member 20A may be a ring rotatably provided on the outer circumference of the cylinder 40.

[0035] With the above configuration, the movable member 20A is positioned on the movable part 60A side relative to the intake valve 63, so that the components of the actuator 100A are concentrated on the movable part 60A side relative to the intake valve 63. Therefore, the actuator 100A can be made more compact compared to, for example, the case where the movable member 20A is positioned on the rear member 65A side relative to the intake valve 63.

[0036] The actuator 100A of this embodiment includes a cam ring 130 located on the opposite side of the intake valve seat 61A from the movable member 20A. The cam ring 130 is mounted on a retaining ring 139 provided on the outer circumference of the cylinder 40 and is configured to rotate about the axis of the cylinder 40 by the driving force transmitted from the drive source 150A. As shown in Figure 5, the cam ring 130 has a cam surface 135 that is inclined with respect to the rotational direction and contacts the movable member 20A. In this embodiment, the cam surface 135 supports the movable member 20. Therefore, as the cam surface 135 slides against the movable member 20A as the cam ring 130 rotates, the cam ring 130 can move the movable member 20A and the intake valve seat 61A (see Figure 3) in the axial direction. In this example, when the cam ring 130 rotates in one direction, the movable member 20 rises together with the intake valve seat 61A, and the range of motion of the intake valve 63 narrows. Then, when the cam ring 130 reverses direction, the contact position between the cam surface 135 and the movable member 20A changes to the lower side. As a result, both the movable member 20 and the intake valve seat 61A move downward, and the range of motion of the intake valve 63 widens. In this embodiment, even after the intake valve seat 61A is placed on the flange 47, the movable member 20A moves further downward (the intake valve seat 61A and the movable member 20A move apart from each other).

[0037] According to the above configuration, since the rotational motion of the cam ring 130 is converted into movement along the axial direction of the movable member 20A, the need to arrange a large number of movable parts of the actuator 100A on the opposite side of the cam ring 130 from the movable member 20A can be reduced. Therefore, the actuator 100A can be made more compact in the axial direction.

[0038] As shown in Figure 5, the actuator 100A of this embodiment includes a linear motion member 140 configured to rotate the cam ring 130 in conjunction with linear movement. The linear motion member 140 is, for example, a rod extending in a direction intersecting the axial direction. The aforementioned drive source 150A is configured to apply driving force to the linear motion member 140 (see Figure 6). The drive source 150A is, for example, a hydraulic cylinder. As the hydraulic cylinder is driven, the position of the linear motion member 140 is switched, and the rotational position of the cam ring 130 is also switched. As a result, the compressor 10A changes between a first state and a second state.

[0039] In this embodiment, a protrusion is provided on either the outer circumferential surface of the cam ring 130 or the outer circumferential surface of the linear motion member 140, and a recess is provided on the other to accommodate the protrusion. As a result, the linear motion member 140, which moves in a straight line, can push the cam ring 130 in the rotational direction, and driving force is transmitted from the drive source 150A to the cam ring 130. In other embodiments, the above-described protrusions and recesses may not be provided. For example, the end face of the cam ring 130 opposite to the cam surface 135 may be inclined with respect to the rotational direction, and the linear motion member 140 may have a contact surface that abuts against this inclined end face. Even in this case, the cam ring 130 can rotate as the linear motion member 140 moves linearly. Furthermore, the drive source 150A may be an air cylinder, a solenoid, or a motor. For example, if a motor is used as the drive source 150A, the amount of movement of the linear motion member 140 can be adjusted steplessly, and the range of motion of the suction valve 63 can be adjusted steplessly.

[0040] With the above configuration, the cam ring 130 rotates simply by the linear motion of the linear motion member 140 driven by the drive source 150A, so the actuator 100A can be simplified in its configuration.

[0041] As shown in Figure 6, in this embodiment, a single linear motion member 140 is configured to rotate the cam rings 130 of each of the multiple cylinders 40 (two cylinders 40 in the example shown in the figure). This reduces the number of drive sources 150A for the actuator 100A, thus simplifying the configuration of the actuator 100A. Note that the adjustment of the gas intake amount is not limited to being performed simultaneously in the multiple cylinders 40. For example, if a configuration is adopted in which the phases of the tapered surfaces of the recesses or protrusions provided on the cam rings 130 are arranged differently among the multiple cylinders 40, and a configuration is adopted in which the amount of movement of the linear motion member 140 can be controlled, the timing of the gas intake amount adjustment can be staggered among the multiple cylinders 40. This makes it possible to finely and flexibly adjust the gas intake amount in each of the multiple cylinders 40. Note that a configuration may be adopted in which the intake amount of one cylinder 40 is narrowed when the linear motion member 140 moves in one direction, and the intake amount of the other cylinder 40 is narrowed when the linear motion member 140 moves in the other direction.

[0042] Returning to Figure 5, in this embodiment, multiple movable members 20A are arranged at equal intervals along the circumferential direction of the cylinder 40. One example of a movable member 20A is a pin extending in the axial direction. The cam surface 135 of the cam ring 130 described above is provided in multiple locations, corresponding to each of the multiple movable members 20A.

[0043] According to the above configuration, each of the multiple cam surfaces 135 slides against each of the multiple movable members 20A, so that the multiple pin-shaped movable members 20A move the intake valve seat 61A. Since the movement of the intake valve seat 61A is performed by multiple movable members 20A, the movement of the intake valve seat 61 can be stabilized.

[0044] The actuator 100A of this embodiment includes a guide 170 configured to guide the movable member 20A in the axial direction. In this embodiment, a plurality of guides 170 are provided corresponding to each of the plurality of movable members 20A. Each guide 170 includes a first guide 171 and a second guide 172 that are spaced apart in the axial direction. The first guide 171 has a projection provided on the outer circumferential surface of the cylinder 40 at a position close to the cam ring 130, and a first guide hole 171A provided in the projection. One end (lower end) of the pin-shaped movable member 20A is positioned inside the first guide hole 171A. The second guide 172 includes a second guide hole 172A provided in the flange 47. The other end (upper end) of the movable member 20A is positioned inside the second guide hole 172A. In this example, the second guide hole 172A is provided between any two of the plurality of flow paths 47A formed in the flange 47.

[0045] According to the above configuration, in the radial direction of the cylinder 40, the movable member 20A is located inside the outer peripheral end of the flange 47. Therefore, the actuator 100A can be made more compact in the radial direction of the cylinder 40.

[0046] <3. Compressors 10B and 10C according to the second embodiment> Refer to Figures 7 and 8 to illustrate the compressors 10B and 10C(10) according to the second embodiment. Figure 7 is a conceptual cross-sectional view of the compressor 10B(10) according to the second embodiment. Figure 8 is a conceptual cross-sectional view of the compressor 10C(10) according to the second embodiment. Note that components similar to those of compressor 10A may be given the same reference numerals in the drawings, and their explanations may be simplified or omitted. Similarly, explanations of the operation and advantages similar to those of compressor 10A may also be omitted.

[0047] <3-1. Overview of the configuration of compressors 10B and 10C> As shown in Figures 7 and 8, in the compressors 10B and 10C(10) according to the second embodiment, the intake valve seat 61B(61) is integrally formed with the outer circumference of the cylinder 40. Although detailed illustrations are omitted, as an example, the intake valve seat 61B has a shape similar to the flange 47 described with reference to Figure 5, and a flow path similar to the flow path 47A is formed therein (however, the second guide hole 172A is not formed). The intake valve seat 61B is configured to seat the intake valve 63.

[0048] As shown in Figures 7 and 8, the compressors 10B and 10C(10) each include a back member 65B and 65C(65) located on the opposite side of the intake valve seat 61B from the intake valve 63. In the second embodiment, the back members 65B and 65C are configured to move up and down relative to the valve plate 44 described above. As an example, the back members 65B and 65C are O-ring shaped and extend continuously around the entire circumference of the cylinder 40.

[0049] In the compressors 10B and 10C according to the second embodiment, the rear members 65B and 65C, among the intake valve seat 61B and the rear members 65B and 65C, move in the axial direction. As a result, the upper end of the movable range of the intake valve seat 61 is adjusted in the axial direction. In other words, the movable range of the intake valve 63 located between the intake valve seat 61B and the rear members 65B and 65C is changed. In the following description of the second embodiment, the rear members 65B and 65C, among the intake valve seat 61B and the rear members 65B and 65C, may be referred to as "movable parts 60B and 60C," respectively. The movable parts 60B and 60C (60) are moved by actuators 100B and 100C (100), which are components of the compressors 10B and 10C.

[0050] According to the above configuration, the compressors 10B and 10C are equipped with actuators 100B and 100C that move the movable parts 60B and 60C, which are rear members 65B and 65C, in the axial direction. The actuators 100B and 100C change the range of motion of the intake valve 63 between the intake valve seat 61B and the rear members 65B and 65C. This makes it possible to change the cross-sectional area of ​​the intake gas flow path Ci formed between the intake valve 63 and the intake valve seat 61B and 61C when the compressor is activated. Thus, compressors 10B and 10C that can adjust the amount of gas intake in cylinder 40 in stages are realized.

[0051] Furthermore, the movable parts 60B and 60C, which are the rear members 65B and 65C, are ring-shaped and extend continuously along the circumferential direction of the cylinder 40. As a result, the number of parts constituting the compressor 10B and 10C is reduced compared to the case where multiple movable parts 60B and 60C are arranged along the circumferential direction, and the configuration of the actuators 100B and 100C can be simplified.

[0052] Furthermore, since the movable parts 60B and 60C are the back members 65B and 65C, there is no need to move the intake valve seat 61B in the axial direction, and the configuration of the actuators 100B and 100C can be simplified.

[0053] <3-2. Details of the configuration of actuators 100B and 100C> As shown in Figures 7 and 8, the actuators 100B and 100C include movable members 20B and 20C (20) that move the movable parts 60B and 60C by the driving force transmitted from the drive sources 150B and 150C. The movable members 20B and 20C can narrow and widen the range of motion of the intake valve 63 by moving the movable parts 60B and 60C, and are located on the side of the movable parts 60B and 60C relative to the intake valve 63 (in the example in Figure 3, on the upper side relative to the intake valve 63). The movable members 20B and 20C in this embodiment are provided in housing holes formed in the valve plate 44 and are arranged in multiples along the circumferential direction of the cylinder 40.

[0054] In the embodiment shown in Figure 7, the rear member 65B includes an inclined surface 77 that extends inclined with respect to the radial direction of the cylinder 40. The rear member 65B is biased toward the opposite side from the intake valve 63 by a spring 78, which is a component of the actuator 100B. This bias prevents the rear member 65B from moving toward the intake valve 63, even when the pressure in the sealed space within the cylinder chamber Sc decreases as the piston 42 descends, for example. Furthermore, the movable member 20B has an opposing inclined surface 29 that abuts against the inclined surface 77 and is configured to move radially. The movable member 20B is operated by a drive source 150B (150), which may be, for example, a hydraulic cylinder, an air cylinder, or a solenoid. When the movable member 20B moves radially inward by obtaining power from the drive source 150B, the opposing inclined surface 29 slides against the inclined surface 77 and pushes down the back member 65B against the biasing force of the spring 78. This narrows the range of motion of the intake valve 63. Conversely, when the movable member 20B moves radially outward, the back member 65B is pushed up by the biasing force of the spring 78, and the range of motion of the intake valve 63 widens. In addition to the biasing force of the spring 78, the back member 65B may also be pushed up by, for example, the increase in pressure in the sealed space within the cylinder chamber Sc due to the rise of the piston 42.

[0055] With the above configuration, as the moving member 20B moves radially, the opposing inclined surface 29 slides against the inclined surface 77, thereby achieving axial movement of the back member 65B. Therefore, the actuator 100B can be simplified. Furthermore, since the movement of the back member 65B is performed by multiple moving members 20B, the back member 65B can be moved more stably.

[0056] In the embodiment shown in Figure 8, the movable member 20C, provided in the housing hole of the valve plate 44, is pivotably mounted. One end 25 of the movable member 20C in the pivoting direction abuts against the rear member 65C from the opposite side of the intake valve 63, and the other end 26 of the movable member 20C abuts against an operating member 49 configured to move axially. The operating member 49 is a component of the actuator 100C(100) and, as an example, is inserted through a guide hole 16A provided in the crankcase 16. The operating member 49 moves axially by a drive source 150C, which may be, for example, a hydraulic cylinder, an air cylinder, or a solenoid. A ring member, such as the cam ring 130 illustrated with reference to Figure 5, may be interposed between the drive source 150C and the operating member 49. The operating member 49 causes the movable member 20C to swing, which moves the back member 65C in the axial direction, changing the range of motion of the intake valve 63.

[0057] As explained above, by positioning the movable members 20B and 20C on the movable part 60B and 60C side relative to the intake valve 63, the components of the actuators 100B and 100C are concentrated on the movable part 60B and 60C side relative to the intake valve 63. Therefore, the actuators 100B and 100C can be made more compact compared to, for example, the case where the movable members 20B and 20C are positioned on the intake valve seat 61B side relative to the intake valve 63.

[0058] In addition, as another example of the second embodiment, the movable part 60B may obtain the force for vertical movement from oil. In this case, oil may be filled into an oil-filled section formed inside the valve plate 44, and the pressure of this oil may be adjusted by driving a hydraulic cylinder. The movable part 60B, which is provided to close the oil-filled section, moves axially in response to fluctuations in the oil pressure.

[0059] <4. Summary> The contents described in some of the embodiments above can be understood, for example, as follows:

[0060] 1) A reciprocating compressor (10) according to at least one embodiment of the present disclosure is A cylinder (40) that forms a cylinder chamber (Sc), An intake valve (63) is provided around the cylinder chamber (Sc), A movable part (60) is configured to move in the axial direction of the cylinder (40), including either an intake valve seat (61) on which the intake valve (63) is seated, or a rear member (65) located on the opposite side of the intake valve seat (61) with the intake valve (63) in between, An actuator (100) moves the movable part (60) in the axial direction to change the range of motion of the intake valve (63) between the intake valve seat (61) and the back member (65). It is equipped with.

[0061] According to the configuration described in 1) above, the range of motion of the intake valve (63) between the intake valve seat (61) and the back member (65) is changed by the actuator (100), thereby changing the flow path cross-sectional area of ​​the intake gas flow path (Ci) formed between the intake valve (63) and the intake valve seat (61) when the actuator is activated. This enables the realization of a reciprocating compressor (10) that can finely adjust the amount of gas intake in the cylinder (40).

[0062] 2) In some embodiments, the reciprocating compressor (10) described in 1) above, The movable part (60) is ring-shaped and extends continuously along the circumferential direction of the cylinder (40).

[0063] According to the configuration described in 2) above, the number of parts constituting the reciprocating compressor (10) is reduced compared to the case where multiple movable parts (60) are arranged along the circumferential direction, thus simplifying the configuration of the actuator (100).

[0064] 3) In some embodiments, the reciprocating compressor (10) described in 1) or 2) above, The actuator (100) includes a moving member (20) that moves the movable part (60) so that the range of motion of the intake valve (63) is narrowed. The movable member (20) is positioned on the movable part (60) side relative to the intake valve (63).

[0065] According to the configuration described in 3) above, the movable member (20) is positioned on the movable part (60) side relative to the intake valve (63), so that the components of the actuator (100) are concentrated on the movable part (60) side relative to the intake valve (63). Therefore, the actuator (100) can be made more compact.

[0066] 4) In some embodiments, a reciprocating compressor (10A) as described in any of 1) to 3) above, The movable part (60) is the intake valve seat (61A).

[0067] According to the configuration in 4) above, there is no need to move the rear member (65A), so the actuator (100A) can be simplified in its configuration.

[0068] 5) In some embodiments, the reciprocating compressor (10A) described in 4) above, The actuator (100A) is A movable member (20A) is located on the opposite side of the intake valve seat (61A) from the rear member (65A) and is configured to move in the axial direction, The movable member (20A) includes a cam ring (130) located on the opposite side from the intake valve seat (61A) and configured to rotate about the axis of the cylinder (40), The cam ring (130) has a cam surface (135) that is inclined with respect to the direction of rotation, and the cam surface (135) slides against the movable member (20A) as it rotates, causing the movable member (20A) and the intake valve seat (61A) to move toward the rear member (65A).

[0069] According to the configuration in 5) above, a configuration is adopted in which the rotational motion of the cam ring (130) is converted into movement along the axial direction of the movable member (20A). This reduces the need to arrange a large number of movable parts constituting the actuator (100A) on the opposite side of the cam ring (130) from the movable member (20A). Therefore, the actuator (100A) can be made more compact in the axial direction.

[0070] 6) In some embodiments, the reciprocating compressor (10A) described in 5) above, The actuator (100A) is A linear motion member (140) is configured to rotate the cam ring (130) in conjunction with linear movement, A drive source (150A) configured to apply driving force to the linear motion member (140) and It also includes.

[0071] According to the configuration in 6) above, the cam ring (130) rotates simply by the linear motion of the linear motion member (140) driven by the drive source (150A), so the actuator (100A) can be simplified in its configuration.

[0072] 7) In some embodiments, the reciprocating compressor (10A) described in 5) or 6) above, Multiple movable members (20A) are arranged along the circumferential direction of the cylinder (40), Multiple cam surfaces (135) are provided, each corresponding to one of the multiple movable members (20A).

[0073] According to the configuration in 7) above, each of the multiple cam surfaces (135) slides against each of the multiple movable members (20A), causing the multiple movable members (20A) to move toward the rear member (65A) together with the intake valve seat (61A). Since the movement of the intake valve seat (61A) is performed by the multiple movable members (20A), the movement of the intake valve seat (61A) can be stabilized.

[0074] 8) In some embodiments, a reciprocating compressor (10A) as described in any of 4) to 7) above, The actuator (100A) includes a guide (170) configured to guide the moving member (20A) in the axial direction.

[0075] According to the configuration described in 8) above, the moving member (20A) is guided in the axial direction by the guide (170), so that the actuator (100A) can move the intake valve seat (61A) more stably.

[0076] 9) In some embodiments, the reciprocating compressor (10A) described in 8) above, The cylinder (40) includes a flange (47) on which the intake valve seat (61A) is mounted. Each of the aforementioned guides (170) is provided in the flange (47) and includes a guide hole (second guide hole 172A) in which the movable member (20A) is positioned on the inside.

[0077] According to the configuration in 9) above, the movable member (20A) is located inward from the outer peripheral end of the flange (47) on which the intake valve seat (61A) is mounted, in the radial direction of the cylinder (40). Therefore, the actuator (100A) can be made more compact in the radial direction of the cylinder (40).

[0078] 10) In some embodiments, a reciprocating compressor (10A) according to any of 1) to 9) above, The rear member (65A) faces radially inward of the cylinder (40) and includes an intake valve guide surface (67) configured to guide the intake valve (63) in the axial direction.

[0079] According to the configuration described in 10) above, the intake valve (63) is guided in the axial direction by the intake valve guide surface (67), so even if the axial distance between the intake valve seat (61A) and the back member (65A) is changed by the actuator (100A), the intake valve (63) can operate stably.

[0080] 11) In some embodiments, a reciprocating compressor (10B, 10C) as described in any of 1) to 3) above, The movable parts (60B, 60C) are the back members (65B, 65C).

[0081] According to the configuration described in 11) above, there is no need to move the intake valve seat (61A), so the actuators (100B, 100C) can be simplified in their configuration.

[0082] 12) In some embodiments, the reciprocating compressor (10B, 10C) described in 11) above, The rear members (65B, 65C) include an inclined surface (77) that is inclined with respect to the radial direction of the cylinder (40), The actuators (100B, 100C) include moving members (20B, 20C) which have opposing inclined surfaces (29) that abut against the inclined surface (77) and are configured to move along the radial direction to move the back members (65B, 65C) in the axial direction.

[0083] According to the configuration described in 12) above, as the moving members (20B, 20C) move radially, the opposing inclined surfaces (29) slide against the contact inclined surface (77), thereby enabling the back members (65B, 65C) to move along the axial direction. Therefore, the actuators (100B, 100C) can be simplified.

[0084] 13) In some embodiments, the reciprocating compressor (10B, 10C) described in 12) above, Multiple movable members (20B, 20C) are arranged along the circumferential direction of the cylinder (40).

[0085] According to the configuration described in 13) above, the movement of the rear members (65B, 65C) is performed by multiple moving members (20B, 20C), so that the rear members (65B, 65C) can be moved more stably. [Explanation of symbols]

[0086] 10: Reciprocating compressor 20: Movable member 29: Opposing Inclined Surface 40 cylinders 47: Flange 60: Moving part 61: Intake valve seat 63: Intake valve 65: Rear component 67: Intake valve guide surface 77: Inclined surface 100: Actuator 130: Camring 135: Cam surface 140: Linear motion member 150: Power source 170: Guide 172A: 2nd guide hole (guide hole) Sc: Cylinder chamber

Claims

1. The cylinders that form the cylinder chamber, An intake valve provided around the cylinder chamber, A piston configured to reciprocate inside the cylinder, A movable part, which includes either an intake valve seat on which the intake valve is seated, or a rear member located on the opposite side of the intake valve seat with the intake valve in between, and which is configured to move in the axial direction of the cylinder, An actuator moves the movable part in the axial direction and changes the range of motion of the intake valve between the intake valve seat and the back member. Equipped with, The actuator is configured to change the range of motion of the intake valve in a cycle that includes an intake stroke in which the intake valve is pushed up from the intake valve seat and gas is drawn into the cylinder chamber through the intake valve seat, and a discharge stroke in which, with the intake valve seated on the intake valve seat, the gas compressed by the piston is discharged from the cylinder chamber through the discharge valve. Reciprocating compressor.

2. The movable part is ring-shaped and extends continuously along the circumferential direction of the cylinder. The reciprocating compressor according to claim 1.

3. The actuator includes a moving member that moves the movable part such that the range of motion of the intake valve is narrowed. The moving member is located on the movable part side with respect to the intake valve. The reciprocating compressor according to claim 1 or 2.

4. The movable part is the intake valve seat. A reciprocating compressor according to any one of claims 1 to 3.

5. A cylinder forming a cylinder chamber, An intake valve provided around the cylinder chamber, A movable part, which includes either an intake valve seat on which the intake valve is seated, or a rear member located on the opposite side of the intake valve seat with the intake valve in between, and which is configured to move in the axial direction of the cylinder, An actuator moves the movable part in the axial direction and changes the range of motion of the intake valve between the intake valve seat and the back member. Equipped with, The movable part is the intake valve seat, The actuator is A movable member is located on the opposite side of the intake valve seat from the rear member and is configured to move in the axial direction, The moving member includes a cam ring located on the opposite side of the intake valve seat from the moving member and configured to rotate about the axis of the cylinder, The cam ring has a cam surface that is inclined with respect to the direction of rotation, and the cam surface that slides against the moving member as it rotates is configured to move the moving member and the intake valve seat toward the rear member. Reciprocating compressor.

6. The actuator is A linear motion member configured to rotate the cam ring in conjunction with linear movement, A drive source configured to apply driving force to the linear motion member and The reciprocating compressor according to claim 5, further comprising:

7. Multiple movable members are arranged along the circumferential direction of the cylinder, The cam surfaces are provided in multiple locations, corresponding to each of the multiple moving members. The reciprocating compressor according to claim 5 or 6.

8. The actuator includes a guide configured to guide the moving member in the axial direction. The reciprocating compressor according to claim 3.

9. A cylinder forming a cylinder chamber, An intake valve provided around the cylinder chamber, A movable part, which includes either an intake valve seat on which the intake valve is seated, or a rear member located on the opposite side of the intake valve seat with the intake valve in between, and which is configured to move in the axial direction of the cylinder, An actuator moves the movable part in the axial direction and changes the range of motion of the intake valve between the intake valve seat and the back member. Equipped with, The actuator includes a moving member that moves the movable part such that the range of motion of the intake valve is narrowed. The moving member is located on the movable part side with respect to the intake valve, The actuator includes a guide configured to guide the moving member in the axial direction, The cylinder includes a flange on which the intake valve seat is mounted, Each of the aforementioned guides is provided in the flange and includes a guide hole in which the moving member is positioned on the inside. Reciprocating compressor.

10. The rear surface member faces radially inward of the cylinder and includes an intake valve guide surface configured to guide the intake valve in the axial direction. A reciprocating compressor according to any one of claims 1 to 9.

11. The movable part is the back member. A reciprocating compressor according to any one of claims 1 to 3.

12. A cylinder forming a cylinder chamber, An intake valve provided around the cylinder chamber, A movable part, which includes either an intake valve seat on which the intake valve is seated, or a rear member located on the opposite side of the intake valve seat with the intake valve in between, and which is configured to move in the axial direction of the cylinder, An actuator moves the movable part in the axial direction and changes the range of motion of the intake valve between the intake valve seat and the back member. Equipped with, The movable part is the back member, The rear member includes an inclined surface that is inclined with respect to the radial direction of the cylinder, The actuator includes a moving member having an opposing inclined surface that contacts the inclined surface, and configured to move along the radial direction to move the back member in the axial direction. Reciprocating compressor.

13. Multiple movable members are arranged along the circumferential direction of the cylinder. The reciprocating compressor according to claim 12.

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