JP2017009264A - Heat pump type steam generation device and operation method of heat pump type steam generation device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat pump type steam generation device and an operation method of the heat pump type steam generation device capable of rapidly increasing a hydraulic pressure of a refrigerating machine oil pump in starting a compressor while preventing occurrence of problems.SOLUTION: A heat pump type steam generation device 10 includes a heat pump portion 16 and a steam generation portion 12, and a compressor 20 is a multicylinder reciprocation type compressor having a capacity control mechanism 64 variably controlling a compression capacity by closing a refrigerant intake passage of a part of cylinders 20a in the plurality of cylinders 20a, and a refrigerating machine oil pump 68 connected to a crank shaft 20c driving a piston 20b of each cylinder 20a. A control portion 18 executing a cylinder deactivation start mode is disposed to deactivate a part of the cylinders 20a of the compressor 20 by driving the capacity control mechanism 64, and operate the compressor 20 with an operation rotational frequency higher than a start rotational frequency under a starting condition not deactivating the cylinder 20a by the capacity control mechanism 64 in starting the compressor 20.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a heat pump steam generator that recovers heat from hot water to generate steam, and an operation method of the heat pump steam generator.

As one of the steam generation apparatuses, there is a heat pump steam generation apparatus that generates steam by collecting heat from warm water such as industrial waste water or waste water such as used cooling water (see, for example, Patent Document 1). In the heat pump steam generator, the evaporator of the heat pump unit functions as an exhaust heat recovery device, where heat is recovered from the heat source hot water into the refrigerant, and the water to be heated is heated by the condenser using the recovered heat. Since steam is generated, there is an advantage that the running cost and CO ₂ emission amount can be reduced as compared with the combustion system steam generating apparatus that generates steam using boiler equipment or the like.

JP 2012-42205 A

  By the way, as a compressor provided in the heat pump steam generator as described above, a refrigerator oil pump is directly connected to a crankshaft that drives a multi-cylinder piston, and lubrication is performed by supplying oil to each part of the compressor with this refrigerator oil pump. There is a configuration to do.

  In the heat pump steam generator using the compressor having this configuration, depending on the temperature and viscosity of the refrigerating machine oil enclosed in the compressor at the time of activation, the refrigerating machine oil within a specified time after the activation, for example, within 90 seconds. There is a concern that the oil pressure of the pump does not rise to a specified value, and the refrigeration oil is not smoothly supplied to the crankshaft, piston, shaft seal, etc. of the compressor, resulting in poor lubrication. Therefore, in order to ensure the hydraulic pressure of the refrigeration machine oil pump at the time of startup, it is conceivable to increase the operating rotational speed of the compressor at the time of startup. However, the amount of refrigerant circulating in the refrigerant path suddenly increases and the compressor There is a concern that liquid compression may occur on the suction side, and there is a concern that air may enter the compressor from the shaft seal due to a negative pressure on the suction side of the compressor.

  For this reason, conventionally, at the time of starting the compressor, it is assumed that the operation is performed at the minimum number of revolutions specified for the compressor. Therefore, there is a demand for a configuration that can prevent the occurrence of problems such as air intrusion due to liquid compression or negative pressure while ensuring good lubrication performance.

  The present invention has been made in consideration of the above-described problems of the prior art, and is capable of quickly increasing the oil pressure of the refrigeration machine oil pump when starting the compressor while preventing the occurrence of problems. Another object of the present invention is to provide a method for operating the heat pump type steam generator.

  A heat pump steam generator according to the present invention includes a compressor that compresses a refrigerant, a condenser that condenses the refrigerant compressed by the compressor, an expansion mechanism that decompresses the refrigerant that has exited the condenser, and recovery from hot water A heat pump unit that annularly connects an evaporator that evaporates the refrigerant with the generated heat, and a steam generation unit that supplies heated water to the condenser and heats the heated water with the refrigerant to generate steam. A heat pump type steam generation device, wherein the compressor drives a capacity control mechanism that variably controls a compression capacity by closing a refrigerant suction path of a part of a plurality of cylinders, and a piston of each cylinder A multi-cylinder reciprocating compressor having a refrigerating machine oil pump coupled to a crankshaft, wherein when the compressor is started, the capacity control mechanism is driven to deactivate some cylinders of the compressor, capacity Operating said compressor at a higher operating rotational speed than the cranking speed at start condition is not carried out cylinders resting by control mechanism, characterized in that it comprises a control means for executing the cylinder deactivation startup mode.

  According to such a configuration, when the cylinder deactivation start mode is executed by the control means, a part of the cylinders of the compressor is deactivated and the operation speed of the compressor becomes higher than the start speed. Be controlled. Thereby, the rotation speed of the compressor can be secured and the oil supply pressure of the refrigerating machine oil pump can be quickly increased, and the occurrence of poor lubrication of the crankshaft and the piston of the compressor at the start can be prevented. Moreover, in this cylinder deactivation start mode, a compression volume suitable for activation can be secured by deactivating some cylinders of the compressor. As a result, the occurrence of liquid compression on the suction side of the compressor can be prevented, and the suction side pressure of the compressor becomes negative, for example, the problem of air entering from the shaft seal into the compressor. Occurrence can also be prevented. In particular, the heat pump type steam generator uses warm water such as waste water as a heat source of the heat pump unit, and generates steam in the steam generation unit with the heat recovered from this hot water. It is easy to carry out, and it exists in the tendency for the on-off frequency of the compressor at the time of starting to increase rather than a general heat pump apparatus. Therefore, by executing the cylinder deactivation start mode at the time of start-up, damage to the compressor can be prevented and smooth operation can be performed.

  The control means further includes a start mode in which the compressor is operated at the start rotation speed without performing cylinder stop by the capacity control mechanism, and selectively executes the cylinder stop start mode and the start mode. It may be a configuration. If it does so, according to the state of a compressor, the control mode at the time of starting can be used properly by starting mode and cylinder deactivation starting mode. As a result, if the conditions are such that the oil pressure of the refrigeration machine oil pump can be quickly increased without executing the cylinder deactivation start mode, the normal start mode is executed, and the operating speed of the compressor is set to the start speed. Power consumption can be suppressed. On the other hand, in a condition where a rapid increase in the oil supply pressure of the refrigerator oil pump cannot be expected, the inside of the compressor can be well lubricated by executing the cylinder deactivation start mode.

  The control means executes the start-up mode when the heat pump unit is started, and the state where the refueling pressure of the refrigerator oil pump is less than a specified value during the start-up mode continues for a set time. It may be configured to shift to the cylinder deactivation start mode. Then, when the compressor is started, the control unit first executes the start mode, and determines the transition to the cylinder deactivation start mode while monitoring the degree of increase in the refueling oil pump pressure at that time. As a result, since the compressor is driven at the starting rotational speed in the starting mode, it is possible to reduce power consumption and operating costs, while shifting to the cylinder deactivation starting mode as necessary can reduce lubrication inside the compressor. Occurrence can be prevented.

  The control means determines whether or not to execute the cylinder deactivation start mode when the compressor is activated, and executes the cylinder deactivation start mode when it is determined that the cylinder deactivation start mode is necessary. When it is determined that the cylinder deactivation start mode is not necessary, the start mode may be executed. Then, in the state where the occurrence of poor lubrication inside the compressor is predicted, it is possible to perform the cylinder deactivation start mode to perform good lubrication, while it is predicted that no lubrication will occur within the compressor. In this state, the normal start-up mode is executed, and the operation cost can be suppressed.

  The control means includes a standby time from the end of the previous operation of the compressor to the current start, a supply pressure of the refrigerating machine oil pump at the start of the compressor, and a suction to the refrigerating machine oil pump at the start of the compressor It is good also as a structure which performs the said necessity determination using at least 1 condition of the refrigerator oil temperature and the main body temperature of the said compressor.

  In the cylinder deactivation start mode, a correlation may be set between a ratio of the number of deactivation cylinders to the number of cylinders of the compressor and an increase ratio of the operation rotation number to the rotation speed of the compressor. That is, for example, when two cylinders of a four-cylinder compressor are stopped by the capacity control mechanism, the operating rotational speed of the compressor is set to twice the starting rotational speed. As a result, since the compression volume is maintained even in the cylinder deactivation start mode, the refueling pressure can be quickly increased while preventing the occurrence of problems such as liquid compression without changing the refrigerant circulation amount in the heat pump unit. .

  In addition, the operation method of the heat pump steam generator according to the present invention includes a compressor, a condenser, an expansion mechanism, and an evaporator connected in a ring shape, and recovers heat from hot water using a heat pump unit in which a refrigerant flows. The heat pump type steam generating device is configured to transmit the heat generated to the water to be heated to generate steam, and at the time of starting the compressor, some cylinders of the compressor are deactivated, and the compressor It is characterized by operating at an operating speed higher than the starting speed.

  A start mode in which the compressor is operated at the start rotation speed without stopping the cylinder when starting the compressor, and a part of the cylinders of the compressor are stopped and the operation rotation speed of the compressor is started. A cylinder deactivation start mode in which the engine is operated at a higher rotational speed than the rotational speed may be selectively executed.

  The start mode is executed when the heat pump unit is started, and the cylinder deactivation start mode is entered when the refueling oil pump pressure is lower than a specified value during the start mode for a set time. It may be migrated.

  When the compressor is started, it is determined whether or not to execute the cylinder deactivation start mode. When it is determined that the cylinder deactivation start mode is necessary, the cylinder deactivation start mode is performed. May be executed when it is determined that execution is not necessary.

  According to the present invention, by executing the cylinder deactivation start mode, it is possible to ensure the operation rotational speed of the compressor and quickly increase the oil supply pressure of the refrigeration oil pump. The occurrence of poor lubrication of the piston can be prevented. In addition, in this cylinder deactivation start mode, it is possible to secure a compression volume suitable for activation by deactivating some cylinders of the compressor, so that liquid compression occurs and air enters the compressor. The occurrence of defects can be prevented.

It is a whole lineblock diagram of the heat pump type steam generating device concerning one embodiment of the present invention. It is a Ph diagram of R245fa as an example of a refrigerant having specific characteristics. It is a partial cross section side view which shows the structural example of a compressor. It is a flowchart which shows the 1st starting control method of the compressor of a heat pump type steam generation apparatus. It is a flowchart which shows the 2nd starting control method of the compressor of a heat pump type steam generation apparatus. It is a flowchart which shows the 3rd starting control method of the compressor of a heat pump type steam generation apparatus.

  DESCRIPTION OF EMBODIMENTS Hereinafter, a heat pump type steam generator according to the present invention will be described in detail with reference to the accompanying drawings by exemplifying a preferred embodiment of the operation control method thereof.

  FIG. 1 is an overall configuration diagram of a heat pump steam generator 10 according to an embodiment of the present invention. The heat pump steam generator 10 is a system that recovers exhaust heat from hot water such as factory waste water and generates steam using the recovered exhaust heat. The generated steam is external steam such as a drying device or a sterilizer. Sent to the use facility.

  As shown in FIG. 1, the heat pump steam generating device 10 generates heat by evaporating water to generate water vapor, and heat is generated from the hot water (heat source hot water) supplied by the hot water supply unit 14 and the hot water supply unit 14. And a heat pump unit 16 that supplies this heat as a heat source for generating steam in the steam generation unit 12, and a control unit 18 that controls the system.

  The heat pump unit 16 collects heat from the hot water, the compressor 20 that compresses the refrigerant, the condenser 22 that condenses the refrigerant compressed by the compressor 20, the expansion mechanism 24 that decompresses the refrigerant that has exited the condenser 22, and Thus, the evaporator 26 that evaporates the refrigerant is connected in a ring shape to circulate the refrigerant. In the present embodiment, a heater 28 is connected between the outlet side of the condenser 22 and the inlet side of the expansion mechanism 24. The expansion mechanism 24 is, for example, an electronic expansion valve.

  The refrigerant that has been compressed by the compressor 20 to a high temperature and high pressure is cooled and condensed by exchanging heat with the water circulating in the steam generation unit 12 in the condenser 22. The refrigerant that has exited the condenser 22 is preheated with water flowing through the water supply path 30 by the heater 28 and further cooled, and then adiabatic expansion is performed by the expansion mechanism 24, and the hot water path 32 of the hot water supply unit 14 is expanded by the evaporator 26. It absorbs heat from the flowing hot water, evaporates and returns to the compressor 20.

  The refrigerant path of the heat pump unit 16 includes a suction pressure sensor 34 and a suction temperature sensor 35 that respectively detect the pressure and temperature of the refrigerant on the suction side of the compressor 20, and a pressure and temperature of the refrigerant on the discharge side of the compressor 20, respectively. A discharge pressure sensor 36 and a discharge temperature sensor 37 for detecting, and an inlet temperature sensor 38 for detecting the temperature of the refrigerant on the inlet side of the expansion mechanism 24 are provided. The operation speed of the compressor 20 is controlled through an inverter (INV) 40 based on the detection values of the sensors 34 to 38 under the control of the control unit 18. The operating rotational speed of the compressor 20 is also controlled by the start mode and the cylinder deactivation start mode by the control unit 18 at the time of starting (starting), details of which will be described later.

  In the case of the present embodiment, as the refrigerant sealed in the refrigerant path of the heat pump unit 16, the isentropic line on the Ph diagram is in the superheated region on the low pressure side, and the saturated gas line on the high pressure side has two or more intersections. Or the refrigerant | coolant containing the single refrigerant | coolant with the characteristic which has a contact point, and a mixed refrigerant | coolant is used. As a refrigerant having such unique characteristics, for example, an isentropic line on the Ph diagram as shown in FIG. 2 is in a superheated region on the low pressure side, and a saturated gas line and two or more points on the high pressure side. R245fa which is a refrigerant having an intersection or a contact can be used. For example, in FIG. 2, the isentropic line A line and the saturated gas line intersect at two points A1 and A2.

  The steam generation unit 12 uses a refrigerant circulating in the heat pump unit 16 as a heat source to evaporate water to generate steam, and a vapor-liquid two-phase flow including water and steam generated by the condenser 22 A water vapor separator 42 that separates into water, a steam supply path 44 that supplies the steam separated by the water vapor separator 42 to an external steam utilization facility, and water that is separated by the water vapor separator 42 is supplied from the water supply path 30. And a water circulation path 46 that joins the water to be led from the condenser 22 to the water vapor separator 42.

  The water vapor separator 42 is formed of a cylindrical container along the vertical direction, and stores water inside the container by supplying water from the water supply path 30 connected to the water circulation path 46 connected to the lower end wall. . In the water supply path 30, water (water supply) from a water pipe or a water tank (not shown) is introduced to the water circulation path 46 through the heater 28 by the water supply pump 48. Under the control of the control unit 18, the feed water pump 48 is operated at its rotational speed via an inverter (INV) 52 based on a detection value (water level) of a water level sensor 50 that measures the water level of water stored in the water vapor separator 42. Is controlled. Connected to the water vapor separator 42 is a pressure relief valve 54 that is opened when the internal vapor pressure exceeds a predetermined pressure.

  The water circulation path 46 includes a liquid pipe 46 a that communicates from the lower end wall of the water vapor separator 42 to the condenser 22, and a vapor pipe 46 b that communicates from the condenser 22 to the upper side wall of the water vapor separator 42. Water flows through the liquid pipe 46a, and a gas-liquid two-phase flow containing water and steam flows through the steam pipe 46b. A circulation pump 56 is provided in the liquid pipe 46a. The operation speed of the circulation pump 56 is controlled through an inverter (INV) 58 under the control of the control unit 18.

  The steam supply path 44 is a path that is connected to the upper end wall of the water vapor separator 42 and is supplied into the water vapor separator 42 from the steam pipe 46b, where the steam after the water is separated is sent out to the outside. A pressure regulating valve 60 that regulates the pressure of the flowing steam is installed in the steam supply path 44. The opening of the pressure regulating valve 60 is adjusted based on the vapor pressure in the water vapor separator 42 measured by the pressure sensor 62 under the control of the control unit 18. By appropriately adjusting the opening degree of the pressure regulating valve 60, the flow rate and pressure of the steam sent out from the heat pump steam generating device 10 can be controlled.

  The control unit (control unit) 18 is a control device that controls the output of the heat pump unit 16 by controlling the operation of the compressor 20 based on the detection values of the sensors 34 to 38, and the water supply pump 48 as described above. The circulation pump 56 and the pressure regulating valve 60 may be controlled, but the steam generation unit 12 side may be controlled by another control unit (not shown).

  Further, when the compressor 20 is started, the control unit 18 controls the start mode for controlling the operation rotational speed and the capacity control mechanism 64 provided in the compressor 20 as shown in FIG. A function of selectively executing the cylinder deactivation start mode in which the deactivation is performed.

  Therefore, a specific configuration example of the compressor 20 will be described next. FIG. 3 is a partial cross-sectional side view illustrating a configuration example of the compressor 20.

  As shown in FIG. 3, the compressor 20 includes a plurality of cylinders 20a in which pistons 20b are arranged to be able to advance and retreat, and a crankshaft 20c that drives the pistons 20b of each cylinder 20a to advance and retreat in a crankcase 20d and an upper part thereof. Capacity control that is a multi-cylinder reciprocating compressor having a configuration housed in a connected cylinder head 20e, and variably controls the compression capacity (displacement) by closing the refrigerant suction path of some cylinders 20a. A mechanism 64 is provided. The compressor 20 according to the present embodiment has a four-cylinder configuration having four cylinders 20 a, and two cylinders are paused by the capacity control mechanism 64. The compressor 20 may be other than four cylinders, for example, six cylinders. In this case, the capacity control mechanism 64 is configured to be able to deactivate two cylinders or four cylinders, for example.

  One end side of the crankshaft 20 c is connected to a pulley 66 through a shaft seal 65. Power from a drive source such as an external motor or engine is transmitted to the pulley 66 via a belt (not shown), thereby rotating the crankshaft 20c. That is, the compressor 20 has an open type configuration.

  The rotor of the refrigerating machine oil pump 68 is connected to the other end side of the crankshaft 20c. The refrigerating machine oil pump 68 is a pump for circulating the refrigerating machine oil enclosed in the crankcase 20d, and each element in the crankcase 20d, for example, by the suction and discharge force by the rotor rotating by the rotation of the crankshaft 20c, for example, Refrigerating machine oil is supplied to the crankshaft 20c, each piston 20b, and the shaft seal 65. Therefore, the operating rotational speed of the refrigerator oil pump 68 matches the operating rotational speed of the compressor 20.

  A specific oil supply path A by the refrigerator oil pump 68 is formed, for example, as shown by a broken line in FIG. That is, the refrigerating machine oil pump 68 sucks refrigerating machine oil in the oil reservoir stored in the bottom of the crankcase 20d from the suction port 68a and discharges it from the discharge port 68b, and passes through the paths formed in the crankshaft 20c. Lubricating refrigeration oil is supplied to the piston 20b and the shaft seal 65 and lubricated, and again forms a path for circulation from the oil reservoir to the suction port 68a.

  The suction port 68a and the discharge port 68b of the refrigerating machine oil pump 68 are respectively provided with hydraulic sensors 69a and 69b serving as pressure detection units, and the detection results are transmitted to the control unit 18. The control unit 18 calculates a differential pressure, which is a difference between detected values of the hydraulic sensor 69a and the hydraulic sensor 69b, as the oil supply pressure. The oil supply pressure can also be obtained as a differential pressure obtained by subtracting the gas pressure in the crankcase 20d detected by a pressure sensor (not shown) from the detection value of the hydraulic sensor 69b at the discharge port 68b.

  The piston 20b of each cylinder 20a, which is inserted in a cylinder 20f formed in the cylinder head 20e so as to be able to advance and retreat, sucks and compresses the refrigerant from the refrigerant path into the compression chamber through the suction valve 72 through the suction port 70, and discharges it. The refrigerant is discharged from the discharge port 76 to the refrigerant path via 74. The capacity control mechanism 64 of the present embodiment is configured by an electromagnetic valve, and the electromagnetic valve is driven and controlled under the control of the control unit 18, thereby closing and fixing the intake valve 72 of the cylinder 20 a that is the target of cylinder deactivation, The compression operation is suspended by restricting the suction of the refrigerant into the compression chamber.

  In the heat pump type steam generator 10 configured as described above, during the steady operation, the heat of the hot water flowing through the hot water path 32 of the hot water supply unit 14 is recovered by the evaporator 26 to the refrigerant by the heat pump unit 16 and recovered to the refrigerant. The generated heat is transferred by the condenser 22 to the water flowing through the water supply path 30 of the steam generation unit 12 to generate steam. Thereby, exhaust heat is efficiently recovered and used, and high energy saving performance is exhibited.

  Such a heat pump type steam generator 10 has an operation method in which the following first to third activation control methods are executed by the control unit 18 at the time of activation. As a result, the oil supply pressure (hydraulic pressure) by the refrigerator oil pump 68 is quickly raised regardless of the temperature and viscosity state of the refrigerator oil in the compressor 20, and the crankshaft 20c, the piston 20b, the shaft seal 65 and the like are frozen. The machine oil is smoothly circulated, and at the same time, the refrigerant circulation amount in the heat pump unit 16 is appropriately controlled to prevent liquid compression of the refrigerant in the compressor 20.

  FIG. 4 is a flowchart showing a first activation control method of the compressor 20 of the heat pump type steam generator 10.

  In the first activation control method, when the heat pump steam generator 10 is started, the control unit 18 activates the compressor 20 (step S1), and first executes the activation mode (step S2).

  This start mode is a control mode for performing a general start-up operation that does not drive the capacity control mechanism 64, and the control unit 18 controls the operation speed of the compressor 20 to the start speed (step S3). The starting rotational speed is a minimum rotational speed that satisfies both the minimum rotational speed defined in advance for each type of the compressor 20 and the minimum operating rotational speed at which refrigerating machine oil pump 68 can ensure oil supply to each element. . That is, when the compressor 20 is operated at a speed lower than the starting rotational speed, the refrigerating machine oil pump 68 does not exhibit the desired performance, and there is a concern that lubrication to each element may be insufficient, resulting in poor lubrication.

  When the compressor 20 is operated in the start mode, the control unit 18 detects the oil supply pressure by the refrigerating machine oil pump 68 (step S4), and when the oil supply pressure is equal to or higher than the specified value (No in step S4), the discharge pressure Based on the detection values of the sensor 36 and the discharge temperature sensor 37, the discharge-side superheat degree of the compressor 20 is obtained. (Step S12). The specified value of the oil supply pressure indicates, for example, the minimum hydraulic pressure necessary for good lubrication of each element of the compressor 20, and if the specified value or more, the normal operation mode is assumed that good lubrication is performed. It is supposed to migrate. The regulation of the oil supply pressure may be one predetermined value, but may be changed according to the refrigerator oil temperature, for example. If the discharge-side superheat degree is less than the specified value in step S11 (No in step S11), the process returns to step S3. The determination of the discharge-side superheat degree in step S11 may be omitted.

  The normal operation mode is a control mode that is executed during steady operation after the start-up process of the heat pump unit 16 is completed. For example, the discharge pressure sensor 36 and the discharge temperature sensor 37 are adjusted by adjusting the opening of the expansion mechanism 24. The operation is continued while adjusting the refrigerant state on the discharge side of the compressor 20 to a degree of superheat equal to or greater than a predetermined value based on the detected value.

  On the other hand, when the refueling pressure detected in step S4 is less than the specified value (Yes in step S4), it is subsequently determined whether or not the set time has elapsed since the start of the compressor 20 (step S4). S5) If the set time has not elapsed, steps S4 and S5 are continued (No in step S5). Then, when the set time has elapsed with the refueling pressure less than the specified value (Yes in step S5), the process shifts to the cylinder deactivation start mode (step S6). The set time in step S5 is a specification that may cause poor lubrication of the crankshaft 20c, the piston 20b, the shaft seal 65, etc. if the oil supply pressure does not exceed the specified value after the start of the compressor 20. The time is set with reference to time (for example, 90 seconds), and is set to about 30 seconds, which is shorter than the specified time, for example.

  The cylinder deactivation start mode is a control mode for performing a start operation in which the capacity control mechanism 64 is driven. The control unit 18 controls the capacity control mechanism 64 to deactivate some cylinders 20a of the compressor 20 (step S7). ), The operating rotational speed of the compressor 20 is controlled to a rotational speed (set rotational speed) higher than the starting rotational speed that is the operating rotational speed in the start mode (step S8).

  In the cylinder deactivation start mode of the present embodiment, the two cylinders of the four-cylinder compressor 20 are deactivated by the capacity control mechanism 64, while the set rotation speed is set to twice the start rotation speed in the start mode. As a result, in the cylinder deactivation start mode, the number of cylinders 20a in which the compressor 20 is driven is halved as compared with that in the start mode, but the operation volume is doubled, so the compression volume is maintained, and the heat pump The refrigerant circulation amount in the part 16 is not changed, and the activation process substantially equivalent to the activation mode is executed. As a result, the number of revolutions of the refrigerating machine oil pump 68 is double that in the start mode and the oil supply pressure increases, so that the refrigerating machine oil can be satisfactorily supplied to the crankshaft 20c, piston 20b, shaft seal 65, and the like. These lubrication failures can be avoided. In addition, although the operation speed of the compressor 20 is increased, the refrigerant circulation amount in the heat pump unit 16 is maintained at the same level as in the start-up mode, thereby preventing the occurrence of liquid compression on the suction side of the compressor 20. In addition, it is possible to avoid a situation in which the suction side pressure of the compressor 20 becomes a negative pressure and air enters from the shaft seal 65 into the compressor 20.

  When the compressor 20 is operated in such a cylinder deactivation start mode, the control unit 18 detects the oil supply pressure by the refrigerating machine oil pump 68 (step S9), and if the oil supply pressure is less than the specified value, the oil supply pressure is detected. And a determination is continued (No of step S9). The specified value of the oil supply pressure indicates, for example, the minimum hydraulic pressure necessary for good lubrication of each element of the compressor 20, and when it is less than the prescribed value, it is assumed that good lubrication is not performed and the cylinder is deactivated. The mode is to continue. The prescription of the oil supply pressure in this case may be one predetermined value, but may be changed according to the refrigerator oil temperature, for example.

  On the other hand, when the refueling pressure detected in step S9 is equal to or higher than the specified value (Yes in step S9), it is subsequently determined whether or not the discharge-side superheat degree of the compressor 20 is equal to or higher than the specified value (step S11). ), When it becomes equal to or greater than the specified value (Yes in step S11), the process shifts to the normal operation mode (step S12). If the discharge-side superheat degree is less than the specified value in step S11 (No in step S11), the process returns to step S3. The determination of the discharge-side superheat degree in step S11 may be omitted. Moreover, you may transfer to the starting mode similar to step S2 and S3 between step S9 and step S11 (step S10).

  Therefore, in the first activation control method, when the compressor 20 is activated, the activation mode is started first, and the shift to the cylinder deactivation activation mode is performed while monitoring the increase in the oil supply pressure of the refrigerator oil pump 68 at that time. to decide. As a result, since the start mode drives the compressor 20 at the start rotation speed, it is possible to reduce power consumption and operation costs, while shifting to the cylinder deactivation start mode as necessary allows lubrication inside the compressor 20. The occurrence of defects can be prevented.

  FIG. 5 is a flowchart showing a second activation control method of the compressor 20 of the heat pump steam generation apparatus 10.

  In the second activation control method, when the operation of the heat pump steam generator 10 is started, the control unit 18 activates the compressor 20 (step S21), and determines whether or not it is necessary to execute the cylinder deactivation activation mode (step S21). S22).

  The necessity determination of step S22 is, for example, the waiting time (condition 1) from the end of the previous operation of the compressor 20 (heat pump type steam generator 10) to the current start, the heat pump unit 16 detected by the hydraulic sensors 69a and 69b. The refrigerating machine oil temperature at the start of the refrigerating machine oil pump 68 (condition 2), the temperature of the refrigerating machine oil sucked into the refrigerating machine oil pump 68 at the time of starting the heat pump unit 16 measured by the temperature sensor 80 (see FIG. 3) (condition 3) , And at least one of the main body temperatures (condition 4) of the compressor 20 measured by the temperature sensor 82 (see FIG. 3).

  For example, in condition 1, when the standby time from the end of the previous operation to the current start is a predetermined time or more, the compressor 20 is sufficiently cooled, and the refrigerating machine oil temperature is low and the viscosity is high. Although it can be determined that it is difficult, even if the waiting time from the end of the previous operation to the current start is less than the predetermined time, the compressor 20 is considerably hot, the temperature of the refrigerating machine oil is high, and the viscosity is low. It can also be determined that the oil supply pressure is difficult to increase, and the setting of such conditions may be appropriately set according to the use conditions of the heat pump steam generator 10. In addition, for conditions 2 to 4, determination conditions are set in consideration of the temperature and viscosity of the refrigerating machine oil as in the case of condition 1.

  When it is determined in step S22 that a rapid increase in the fuel pressure cannot be expected and it is necessary to execute the cylinder deactivation control mode (Yes in step S22), the cylinder deactivation control mode in steps S23 to S26 is subsequently performed. The Since these steps S23 to S26 are the same as the cylinder deactivation start mode (steps S6 to S9 in FIG. 4) in the first start control method described above, detailed description thereof is omitted. Further, control steps similar to steps S10 and S11 in FIG. 4 may be executed following step S26.

  And when the oil supply pressure detected by step S26 is more than a regulation value (Yes of step S26), it transfers to normal operation mode (step S29). This normal operation mode is also the same as the normal operation mode (step S12 in FIG. 4) in the first activation control method described above.

  On the other hand, if it is determined in step S22 that a rapid increase in the refueling pressure is expected and it is not necessary to execute the cylinder deactivation control mode (No in step S22), the control unit 18 executes the start mode (step S27). Then, the operating rotational speed of the compressor 20 is controlled to the starting rotational speed (step S28). Since these steps S27 to S28 are the same as the activation mode (steps S2 to S3 in FIG. 4) in the first activation control method described above, detailed description thereof is omitted. And after completion | finish of starting mode, it transfers to normal operation mode (step S29). The transition from the start mode to the normal operation mode may also be executed when the oil supply pressure becomes equal to or higher than the predetermined value, similarly to step S4 in the first start control method described above. You may perform when the superheat degree of the discharge side of the compressor 20 becomes more than a regulation value.

  Therefore, in the second activation control method, when the compressor 20 is activated, the necessity of the cylinder deactivation activation mode is first determined. Therefore, the cylinder deactivation activation is predicted in the state where occurrence of poor lubrication within the compressor 20 is predicted. While the mode can be executed and good lubrication can be performed, the normal start-up mode can be executed in a state where it is predicted that the occurrence of poor lubrication in the compressor 20 will not occur, and the operating cost can be suppressed.

  FIG. 6 is a flowchart showing a third start-up control method for the compressor 20 of the heat pump steam generator 10.

  In the third start control method, the control unit 18 does not execute the normal start mode or does not have the normal start mode program itself, and only the cylinder deactivation start mode is executed. That is, step S41 in FIG. 6 is the same as step S1 in FIG. 4, and steps S42 to S45 in FIG. 6 are the same as steps S6 to S9 in FIG. Further, after executing step S45 and a control step similar to step S11 in FIG. 4, the process may proceed to step S46. Step S46 is the same as step S12 in FIG.

  Therefore, in the third start control method, since the cylinder deactivation start mode is always executed when the compressor 20 is started, it is possible to prevent the occurrence of poor lubrication inside the compressor 20.

  As described above, the heat pump steam generation device 10 according to the present embodiment includes the heat pump unit 16 and the steam generation unit 12, and the compressor 20 sucks the refrigerant in some of the cylinders 20a. A multi-cylinder reciprocating compressor having a capacity control mechanism 64 that variably controls the compression capacity by closing a path, and a refrigeration oil pump 68 connected to a crankshaft 20c that drives a piston 20b of each cylinder 20a; When the compressor 20 is started, the capacity control mechanism 64 is driven to stop some cylinders 20a of the compressor 20, and the cylinder stop start mode for setting the operation speed of the compressor 20 higher than the start speed is set. The control part 18 to perform is provided.

  Therefore, in the heat pump steam generation device 10, when the cylinder deactivation start mode is executed by the control unit 18, some cylinders 20a of the compressor 20 are deactivated, and the operation rotation speed of the compressor 20 is set to the start rotation speed. It is controlled to be higher than that. As a result, the operating rotational speed of the compressor 20 can be ensured and the oil supply pressure of the refrigeration machine oil pump 68 can be quickly increased, and the occurrence of poor lubrication of the crankshaft 20c and the piston 20b of the compressor 20 at the start can be prevented. it can. Moreover, in this cylinder deactivation start mode, a compression volume suitable for activation can be secured by deactivating some cylinders 20a of the compressor 20. As a result, the occurrence of liquid compression on the suction side of the compressor 20 can be prevented, and the suction side pressure of the compressor 20 becomes negative, so that air enters the compressor 20 from the shaft seal 65. It is possible to prevent the occurrence of malfunctions.

  In particular, the heat pump steam generator 10 uses hot water such as factory wastewater supplied from the hot water path 32 as a heat source of the heat pump unit 16, and generates steam in the steam generator 12 with the heat recovered from the hot water. In addition, the flow rate and temperature of the hot water serving as a heat source are likely to fluctuate, and the on / off frequency of the compressor 20 at the time of startup tends to increase as compared with a general heat pump device. Therefore, by executing the cylinder deactivation start mode at the time of start-up, damage to the compressor 20 can be prevented and smooth operation can be performed.

  In the heat pump type steam generator 10, as a refrigerant circulating in the heat pump unit 16, an isentropic line on the Ph diagram is in the superheated region on the low pressure side and two or more intersections with the saturated gas line on the high pressure side. Or what has the characteristic which has a contact is used. When a refrigerant having such characteristics is used, a general refrigerant such that the refrigerant may be liquefied and liquid-compressed during the compression stroke of the compressor 20 depending on the degree of overheating even if the suction side is in an overheated state. However, the occurrence of liquid compression can be prevented by executing the cylinder deactivation start mode during start-up. In addition, with the refrigerant having such characteristics, if the operating speed of the compressor 20 is greatly increased at the time of startup, the suction side pressure is likely to be negative, and the concern of air entering from the shaft seal 65 is further increased. By executing the pause operation mode, it is possible to quickly increase the oil supply pressure of the refrigerator oil pump 68 while avoiding such problems.

  In the cylinder deactivation start mode of the heat pump steam generator 10, there is a correlation between the ratio of the deactivation cylinder number to the number of cylinders 20a of the compressor 20 and the increase ratio of the operation rotation number to the start rotation number of the compressor 20. Is set. That is, when the two cylinders of the four-cylinder compressor 20 are stopped by the capacity control mechanism 64, the operating speed of the compressor 20 is set to twice the operating speed (starting speed) in the start mode. . As a result, since the compression volume is maintained even in the cylinder deactivation start mode, it is possible to quickly increase the fuel supply pressure while preventing the occurrence of problems such as liquid compression without changing the refrigerant circulation amount in the heat pump unit 16. it can. Therefore, for example, when the compressor 20 has 6 cylinders and 2 cylinders are deactivated, the operating rotational speed is set to 4/3 times the starting rotational speed, and when 4 cylinders among 6 cylinders are deactivated, the operational rotational speed is If it is set to 5/3 times the starting rotational speed, a compression volume equivalent to that in the starting mode is maintained.

  In the heat pump steam generating apparatus 10, the control unit 18 operates the compressor 20 at a lower operating rotational speed than the cylinder deactivation start mode without deactivating the cylinder 20a by the capacity control mechanism 64 when the compressor 20 is activated. For example, a start mode for operating at the start speed and a cylinder deactivation start mode are selectively executed. Thereby, according to the state of the compressor 20, the control mode at the time of starting can be used properly by starting mode and cylinder deactivation starting mode. As a result, in a condition where the refueling pressure of the refrigeration machine oil pump 68 can be quickly increased without executing the cylinder deactivation start mode, the normal start mode is executed to suppress the operation speed of the compressor 20. , Power consumption can be suppressed. On the other hand, in a condition where a rapid increase in the oil supply pressure of the refrigerator oil pump 68 cannot be expected, the inside of the compressor 20 can be well lubricated by executing the cylinder deactivation start mode.

  It should be noted that the present invention is not limited to the above-described embodiment, and it is needless to say that the present invention can be freely changed without departing from the gist of the present invention.

DESCRIPTION OF SYMBOLS 10 Heat pump type steam generator 12 Steam generation part 14 Hot water supply part 16 Heat pump part 18 Control part 20 Compressor 20a Cylinder 20b Piston 20c Crankshaft 20d Crankcase 20e Cylinder head 20f Cylinder 22 Condenser 24 Expansion mechanism 26 Evaporator 28 Heater 30 Water Supply Path 32 Hot Water Path 40, 52, 58 Inverter 42 Steam Separator 44 Steam Supply Path 46 Water Circulation Path 65 Shaft Seal 68 Refrigerator Oil Pump 68a Suction Port 68b Discharge Port 70 Suction Port 72 Suction Valve 74 Discharge Valve 76 Discharge Port

Claims (10)

A compressor that compresses the refrigerant, a condenser that condenses the refrigerant compressed by the compressor, an expansion mechanism that decompresses the refrigerant that has exited the condenser, and an evaporator that evaporates the refrigerant with heat recovered from hot water A heat pump connected to
A heat pump type steam generating device comprising: a water to be heated to the condenser; and a steam generating unit configured to generate steam by heating the water to be heated by the refrigerant,
The compressor includes a capacity control mechanism that variably controls a compression capacity by closing a refrigerant suction path of a part of the plurality of cylinders, and a refrigerating machine oil coupled to a crankshaft that drives a piston of each cylinder. A multi-cylinder reciprocating compressor having a pump,
At the time of starting the compressor, the capacity control mechanism is driven to stop some cylinders of the compressor, and the operation speed is higher than the start speed in the start condition in which the cylinders are not stopped by the capacity control mechanism. A heat pump type steam generating apparatus comprising control means for operating the compressor and executing a cylinder deactivation start mode. In the heat pump type steam generator according to claim 1,
The control means further includes a start mode in which the compressor is operated at the start rotation speed without performing cylinder stop by the capacity control mechanism, and selectively executes the cylinder stop start mode and the start mode. A heat pump steam generator characterized by that. In the heat pump type steam generator according to claim 2,
The control means executes the start-up mode when the heat pump unit is started, and the state where the refueling pressure of the refrigerator oil pump is less than a specified value during the start-up mode continues for a set time. A heat pump type steam generator characterized by shifting to a cylinder deactivation start mode. In the heat pump type steam generator according to claim 2,
The control means determines whether or not to execute the cylinder deactivation start mode when the compressor is activated, and executes the cylinder deactivation start mode when it is determined that the cylinder deactivation start mode is necessary. When it is determined that the cylinder deactivation start mode is unnecessary, the start mode is executed. In the heat pump type steam generator according to claim 4,
The control means includes a standby time from the end of the previous operation of the compressor to the current start, a supply pressure of the refrigerating machine oil pump at the start of the compressor, and a suction to the refrigerating machine oil pump at the start of the compressor The heat pump type steam generating device, wherein the necessity determination is performed using at least one condition of a temperature of the refrigerating machine oil and a temperature of the main body of the compressor. In the heat pump type steam generator according to any one of claims 1 to 5,
In the cylinder deactivation start mode, a correlation is set between a ratio of the deactivation cylinder number to the cylinder number of the compressor and an increase ratio of the operation rotation number to the start rotation number of the compressor. Heat pump steam generator. A heat pump type in which a compressor, a condenser, an expansion mechanism, and an evaporator are connected in an annular shape, and heat is recovered from hot water using a heat pump unit through which refrigerant flows, and the recovered heat is transmitted to heated water to generate steam. A method of operating a steam generator,
Operation of a heat pump steam generator characterized in that at the time of starting up the compressor, some cylinders of the compressor are deactivated and the operation speed of the compressor is operated at a speed higher than the start speed. Method. In the operation method of the heat pump type steam generator according to claim 7,
A start mode in which the compressor is operated at the start rotation speed without stopping the cylinder when starting the compressor, and a part of the cylinders of the compressor are stopped and the operation rotation speed of the compressor is started. A method for operating a heat pump steam generator, wherein a cylinder deactivation start mode that operates at a rotational speed higher than the rotational speed is selectively executed. In the operation method of the heat pump type steam generator according to claim 8,
The start mode is executed when the heat pump unit is started, and the cylinder deactivation start mode is entered when the refueling oil pump pressure is lower than a specified value during the start mode for a set time. A method for operating a heat pump steam generator, characterized in that it is shifted. In the operation method of the heat pump type steam generator according to claim 8,
When the compressor is started, it is determined whether or not to execute the cylinder deactivation start mode. When it is determined that the cylinder deactivation start mode is necessary, the cylinder deactivation start mode is performed. The operation method of the heat pump steam generator is characterized in that the start-up mode is executed when it is determined that the operation is not necessary.

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